U.S. patent number 3,912,227 [Application Number 05/407,051] was granted by the patent office on 1975-10-14 for motion compensation and/or weight control system.
This patent grant is currently assigned to Drilling Systems International, Inc.. Invention is credited to Michael Donahoo Keen, Larry E. Lee, Roderick Charles LeJeune, Joseph Fitzpatrick Meeker.
United States Patent |
3,912,227 |
Meeker , et al. |
October 14, 1975 |
Motion compensation and/or weight control system
Abstract
A motion compensation and/or weight control system mounted from
a load-supporting assembly for supporting a load which is movable
relative to the load-supporting assembly. The motion compensation
and/or weight control system comprises an improved expansible and
contractible mechanism mounted between the load-supporting assembly
and its load. The improved expansible and contractible mechanism
includes a passively operated piston and cylinder assembly for
supporting the load and an actively operated piston and cylinder
assembly for providing biasing forces. The system may be operated
either in the pressure mode or in the position mode. When the
system is operated in the position mode, hydraulic fluid is
actively supplied to and withdrawn from the piston and cylinder
assembly responsive to the velocity of the expansion and
contraction of the expansible and contractible mechanism and the
velocity of the vertical movement of the floating structure
relative to the earth.
Inventors: |
Meeker; Joseph Fitzpatrick
(Seabrook, TX), Keen; Michael Donahoo (Houston, TX), Lee;
Larry E. (Houston, TX), LeJeune; Roderick Charles
(Alvin, TX) |
Assignee: |
Drilling Systems International,
Inc. (Houston, TX)
|
Family
ID: |
23610408 |
Appl.
No.: |
05/407,051 |
Filed: |
October 17, 1973 |
Current U.S.
Class: |
254/271; 175/5;
254/337; 254/900; 60/413; 254/277; 254/361 |
Current CPC
Class: |
E21B
19/09 (20130101); F15B 21/087 (20130101); Y10S
254/90 (20130101) |
Current International
Class: |
E21B
19/00 (20060101); E21B 19/09 (20060101); F15B
21/00 (20060101); F15B 21/08 (20060101); B66D
001/50 () |
Field of
Search: |
;254/172,173R
;175/27,5,7 ;173/4,6 ;60/325,413,416 ;91/390 ;92/108,110,134
;267/124,125 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Wood, Jr.; M. Henson
Assistant Examiner: Reese; Randolph A.
Attorney, Agent or Firm: Edwards; Joe E. Martin; Julian
Clark
Claims
What is claimed is:
1. in a load-supporting assembly for supporting a load which is
movable relative to the load-supporting assembly, an improved
motion compensation and/or weight control system, comprising:
an outer cylinder having end plates at either end thereof;
an inner cylinder disposed concentrically within the outer cylinder
and depending from the first end plate;
a cylindrical piston rod slidably disposed around the inner
cylinder and extending through the second end plate of the outer
cylinder for longitudinal movement relative thereto;
one of the outer cylinder or the piston rod being mounted for
movement with the load-supporting assembly and the other of the
outer cylinder or the piston rod being mounted for movement with
the load;
a first piston secured to the piston rod within the annular chamber
between the inner cylinder and the outer cylinder and slidably
sealed against the outer cylinder;
means for slidably sealing the piston rod against the inner
cylinder;
means for slidably sealing the piston rod against the second end
plate of the outer cylinder;
a second piston secured to and sealing the end of the piston rod
opposite the end of the piston rod to which the first piston is
secured;
the variable volume annular chamber formed between the piston rod,
the first piston, the outer cylinder, and the second end plate of
the outer cylinder, being the primary chamber;
the variable volume chamber formed within the first end plate of
the outer cylinder, the inner cylinder, the piston rod, and the
second piston, being the secondary chamber;
means in fluid communication with the primary chamber for passively
supplying fluid under pressure to the primary chamber whereby force
is supplied against the first piston tending to move the piston rod
in the direction to support the load; and
means in fluid communication with the secondary chamber for
actively supplying fluid into and allowing the withdrawal of fluid
out of the secondary chamber whereby a biasing force may be
supplied against the second piston tending to move the piston rod
in the direction opposing the support of the load.
2. In a load-supporting assembly for supporting a load which is
movable relative to the load-supporting assembly, an improved
motion compensation and/or weight control system according to claim
1 wherein the means for passively supplying fluid under pressure to
the primary chamber includes:
a pneumatic accumulator; and
a pneumatic-hydraulic interface means in fluid communication with
the pneumatic-accumulator interface means and the primary
chamber.
3. In a load supporting assembly for supporting a load which is
movable relative to the load-supporting assembly, an improved
motion compensation and/or weight control system according to claim
1, wherein the means for actively supplying fluid into and allowing
the withdrawal of fluid out of the secondary chamber includes:
a source of hydraulic fluid;
a variable volume, bi-directional pump in fluid communication with
the source of hydraulic fluid and in fluid communication with the
active chamber; and
a control means for controlling the direction and the volume of the
hydraulic fluid pumped by such pump.
4. In a load-supporting assembly for supporting a load which is
movable relative to the load-supporting assembly, an improved
motion compensation and/or weight control system according to claim
1 wherein the means for actively supplying fluid into and allowing
the withdrawal of fluid out of the secondary chamber includes:
a piston and cylinder assembly forming a variable volume
compensating chamber; and
a conduit connecting the compensating chamber and the secondary
chamber;
the compensating chamber, the secondary chamber, and the
interconnecting conduit being filled with hydraulic fluid.
5. In a load-supporting assembly for supporting a load which is
movable relative to the load-supporting assembly, an improved
motion compensation and/or weight control system, comprising:
an outer cylinder having end plates at either end thereof;
an inner cylinder disposed concentrically within the outer cylinder
and depending from the first end plate;
a cylindrical piston rod slidably disposed around the inner
cylinder and extending through the second end plate of the outer
cylinder for longitudinal movement relative thereto;
one of the outer cylinder or the piston rod being mounted for
movement with the load-supporting assembly and the other of the
outer cylinder or the piston rod being mounted for movement with
the load;
a first piston secured to the piston rod within the annular chamber
between the inner cylinder and the outer cylinder and slidably
sealed against the outer cylinder;
means for slidably sealing the piston rod against the inner
cylinder;
means for slidably sealing the piston rod against the second end
plate of the outer cylinder;
a second piston secured to and sealing the end of the piston rod
opposite the end of the piston rod to which the first piston is
secured;
the variable volume annular chamber formed between the piston rod,
the first piston, the outer cylinder, and the second end plate of
the outer cylinder, being the primary chamber;
the variable volume chamber formed within the first end plate of
the outer cylinder, the inner cylinder, the piston rod, and the
second piston, being the secondary chamber;
means for passively supplying fluid under pressure to the primary
chamber; and
means for providing fluid communication between the primary chamber
and the secondary chamber.
6. In a load-supporting assembly for supporting a load which is
movable relative to the load-supporting assembly, an improved
motion compensation and/or weight control system, comprising:
an outer cylinder having end plates at either end thereof;
an inner cylinder disposed concentrically within the outer cylinder
and depending from the first end plate;
a cylindrical piston rod slidably disposed around the inner
cylinder and extending through the second end plate of the outer
cylinder for longitudinal movement relative thereto;
one of the outer cylinder or the piston rod being mounted for
movement with the load-supporting assembly and the other of the
outer cylinder or the piston rod being mounted for movement with
the load;
a first piston secured to the piston rod within the annular chamber
between the inner cylinder and the outer cylinder and slidably
sealed against the outer cylinder;
means for slidably sealing the piston rod against the inner
cylinder;
means for slidably sealing the piston rod against the second end
plate of the outer cylinder;
a second piston secured to and sealing the end of the piston rod
opposite the end of the piston rod to which the first piston is
secured;
the variable volume annular chamber formed between the piston rod,
the first piston, the outer cylinder, and the second end plate of
the outer cylinder, being the primary chamber,
the variable volume chamber formed within the first end plate of
the outer cylinder, the inner cylinder, the piston rod, and the
second piston, being the secondary chamber;
means in fluid communication with the primary chamber for passively
supplying fluid under pressure to the primary chamber whereby force
is supplied against the first piston tending to move the piston rod
in the direction to support the load;
a first pressure tranducer for sensing the pressure of the fluid in
the primary chamber and for generating a first electrical signal
proportional thereto;
means in fluid communication with the secondary chamber for
actively supplying fluid under pressure into and allowing the
withdrawal of such fluid from the secondary chamber whereby a
biasing force may be supplied against the second piston tending to
move the piston rod in the direction opposing the support of the
load;
a second pressure transducer for sensing the pressure of the fluid
in the secondary chamber and for generating a second electrical
signal proportional thereto; and
control means operable responsive to the first and second
electrical signals for controlling the means which actively
supplies the fluid into and allows the withdrawal of the fluid from
the secondary chamber.
7. In a load-supporting assembly for supporting a load which is
movable relative to the load-supporting assembly, an improved
motion compensation and/or weight control system according to claim
6, including:
adjustable means for generating a third electrical signal
proportional to a selected hook load carried by the system; and
wherein the control means are operable responsive to the first,
second and third electrical signals to cause the fluid to be
actively supplied into and withdrawn from the secondary
chamber.
8. In a load-supporting assembly for supporting a load which is
movable relative to the load-supporting assembly, an improved
motion compensation and/or weight control system, comprising:
an outer cylinder having end plates at either end thereof;
an inner cylinder disposed concentrically within the outer cylinder
and depending from the first end plate;
a cylindrical piston rod slidably disposed around the inner
cylinder and extending through the second end plate of the outer
cylinder for longitudinal movement relative thereto;
one of the outer cylinder or the piston rod being mounted for
movement with the load-supporting assembly and the other of the
outer cylinder or the piston rod being mounted for movement with
the load;
a first piston secured to the piston rod within the annular chamber
between the inner cylinder and the outer cylinder and slidably
sealed against the outer cylinder;
means for slidably sealing the piston rod against the inner
cylinder;
means for slidably sealing the piston rod against the second end
plate of the outer cylinder;
a second piston secured to and sealing the end of the piston rod
opposite the end of the piston rod to which the first piston is
secured;
the variable volume annular chamber formed between the piston rod,
the first piston, the outer cylinder, and the second end plate of
the outer cylinder, being the primary chamber;
the variable volume chamber formed within the first end plate of
the outer cylinder, the inner cylinder, the piston rod, and the
second piston, being the secondary chamber;
means for determining the direction and velocity of the movement of
the piston rod relative to the outer cylinder and for generating an
electrical signal proportional thereto;
means in fluid communication with the primary chamber for passively
supplying fluid under pressure to the primary chamber whereby force
is supplied against the first piston tending to move the piston rod
in the direction to support the load;
means in fluid communication with the primary chamber for actively
supplying fluid into and allowing the withdrawal of fluid from the
secondary chamber whereby a biasing force may be applied against
the second piston tending to move the piston rod in the direction
opposing the support of the load; and
control means operable responsive to the electrical signal for
controlling the means which actively supplies fluid into and allows
the withdrawal of fluid out of the secondary chamber.
9. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system, comprising:
a primary piston and cylinder assembly interposed between the
traveling block and the load, one of the primary piston and the
primary cylinder being mounted for movement with the traveling
block and the other of a primary piston and the primary cylinder
being mounted for movement with the load;
a secondary piston and cylinder assembly interposed between the
traveling block and the load, the secondary cylinder being disposed
concentrically within the primary cylinder, one of the secondary
piston and the secondary cylinder being mounted for movement with
the traveling block and the other of the secondary piston and the
secondary cylinder being mounted for movement with the load;
a cylindrical piston rod slidably disposed around the secondary
cylinder and extending beyond the primary cylinder for longitudinal
movement relative to the primary and secondary cylinders;
the primary piston being secured to the end of the piston rod
within the annular chamber between the primary cylinder and the
secondary cylinder and slidably sealed against the primary
cylinder;
the secondary piston being secured to and sealing the end of the
piston rod opposite the end of the piston rod to which the primary
piston is secured;
means for passively maintaining fluid under pressure in the primary
cylinder and on a selected side of the primary piston whereby force
is provided against the primary piston tending to move the primary
piston longitudinally relative to the primary and secondary
cylinders in the direction to support the load; and
means for actively supplying fluid into the secondary cylinder and
onto a selected side of the secondary piston and allowing the
withdrawal of fluid from the secondary cylinder whereby force is
provided against the secondary piston for moving the secondary
piston longitudinally relative to the primary and secondary
cylinders in the direction to oppose the supporting of the
load.
10. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 9,
wherein the means for passively maintaining fluid under pressure in
the primary cylinder and on a selected side of the primary piston
includes:
a pneumatic accumulator;
a pneumatic-hydraulic interface means in fluid communication with
the pneumatic accumulator; and
means for providing fluid communication between the
pneumatic-hydraulic interface means and the primary cylinder.
11. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 9,
wherein the means for actively introducing fluid into the secondary
cylinder and allowing the withdrawal of fluid from the secondary
cylinder includes:
a source of hydraulic fluid;
a variable volume, bi-directional pump in fluid communication with
the active cylinder; and
control means coupled to the pump for controlling the direction and
the volume of the hydraulic fluid pumped by such pump.
12. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 9
wherein the means for actively introducing fluid under pressure
into the secondary cylinder and allowing the withdrawal of fluid
from the secondary cylinder includes:
an auxiliary piston and cylinder assembly forming an auxiliary
variable volume chamber, one of the auxiliary piston and the
auxiliary cylinder being supported in a fixed position relative to
the floating structure and the other of the auxiliary piston and
the auxiliary cylinder being fixed relative to the earth; and
a conduit providing fluid communicatioon between the auxiliary
variable volume chamber and the secondary cylinder.
13. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system, comprising:
a primary piston and cylinder assembly interposed between the
traveling block and the load, one of the primary piston and the
primary cylinder being mounted for movement with the traveling
block and the other of the primary piston and the primary cylinder
being mounted for movement with the load;
means for passively maintaining fluid under pressure in the primary
cylinder and on a selected side of the primary piston whereby force
is provided against the primary piston for moving the primary
piston longitudinally relative to the primary cylinder in the
direction to support the load;
a secondary piston and cylinder assembly interposed between the
traveling block and the load, one of the secondary piston and the
secondary cylinder being mounted for movement with the traveling
block and the other of the secondary piston and the secondary
cylinder being mounted for movement with the load;
the primary and secondary pistons being operatively connected for
coordinated movement;
means for actively introducing fluid into the secondary cylinder
and onto a selected side of the secondary piston and allowing the
withdrawal of the fluid from the secondary cylinder whereby force
is provided against the secondary piston tending to move the
secondary piston longitudinally relative to the secondary cylinder
in the direction to oppose the supporting of the load;
transducer means for determining the pressure of the fluid in the
primary cylinder and for generating a first electrical signal
proportional thereto;
transducer means for determining the pressure of the fluid in the
secondary cylinder and for generating a second electrical signal
proportional thereto;
adjustable means for generating a third electrical signal
proportional to a selected hook load; and
control means operable responsive to the first, second, and third
electrical signals to cause the fluid to be actively supplied into
and withdrawn from the secondary chamber.
14. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 13,
wherein the means for passively maintaining fluid under pressure in
the primary cylinder and on a selected side of the primary piston
includes:
a pneumatic accumulator;
a pneumatic-hydraulic interface means in fluid communication with
the pneumatic accumulator; and
means for providing fluid communication between the
pneumatic-hydraulic interface means and the primary cylinder.
15. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 13,
wherein the means for actively introducing fluid into the secondary
cylinder and allowing the withdrawal of fluid from the secondary
cylinder includes:
a source of hydraulic fluid;
a variable volume, bi-directional pump in fluid communication with
the active cylinder; and
control means coupled to the pump for controlling the direction and
the volume of the hydraulic fluid pumped by such pump.
16. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 13
wherein the means for actively introducing fluid under pressure
into the secondary cylinder and allowing the withdrawal of fluid
from the secondary cylinder includes:
an auxiliary piston and cylinder assembly forming an auxiliary
variable volume chamber, one of the auxiliary piston and the
auxiliary cylinder being supported in a fixed position relative to
the floating structure and the other of the auxiliary piston and
the auxiliary cylinder being fixed relative to the earth; and
a conduit providing fluid communication between the auxiliary
variable volume chamber and the secondary cylinder.
17. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system, comprising:
a primary piston and cylinder assembly interposed between the
traveling block and the load, one of the primary piston and the
primary cylinder being mounted for movement with the traveling
block and the other of the primary piston and the primary cylinder
being mounted for movement with the load;
means for passively maintaining fluid under pressure in the primary
cylinder on a selected side of the primary piston whereby force is
exerted against the primary piston tending to move the primary
piston longitudinally relative to the primary cylinder in the
direction to support the load;
a secondary piston and cylinder assembly interposed between the
traveling block and the load, one of the secondary piston and the
secondary cylinder being mounted for movement with the traveling
block and the other of the secondary piston and the secondary
cylinder being mounted for movement with the load;
means for actively introducing fluid into the secondary cylinder on
a selected side of the secondary piston and allowing the withdrawal
of fluid from the secondary cylinder whereby force is exerted
against the secondary piston tending to move the secondary piston
longitudinally relative to the secondary cylinder in the direction
to oppose the supporting of the load;
means operatively connecting the primary and secondary pistons
together whereby their longitudinal movement is coordinated
together;
means associated with the floating structure for determining the
direction and velocity of the vertical movement of the floating
structure relative to the earth and for generating a first
electrical signal proportional thereto;
means associated with the motion compensation system for
determining the direction and the velocity of the vertical movement
of the load relative to the traveling block and for generating a
second electrical signal proportional thereto; and
control means operable responsive to the first and second
electrical signals for causing the fluid to be actively introduced
into the secondary cylinder and allowing the withdrawal of the
fluid from the secondary cylinder.
18. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 17,
wherein the means for passively maintaining fluid under pressure in
the primary cylinder and on a selected side of the primary piston
includes:
a pneumatic accumulator;
a pneumatic-hydraulic interface means in fluid communication with
the pneumatic accumulator; and
means for providing fluid communication between the
pneumatic-hydraulic interface means and the primary cylinder.
19. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 17,
wherein the means for actively introducing fluid into the secondary
cylinder and allowing the withdrawal of fluid from the secondary
cylinder includes:
a source of hydraulic fluid;
a variable volume, bi-directional pump in fluid communication with
the active cylinder; and
control means coupled to the pump for controlling the direction and
the volume of the hydraulic fluid pumped by such pump.
20. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 17,
wherein the means for actively introducing fluid under pressure
into the secondary cylinder and allowing the withdrawal of fluid
from the secondary cylinder includes:
an auxiliary piston and cylinder assembly forming an auxiliary
variable volume chamber, one of the auxiliary piston and the
auxiliary cylinder being supported in a fixed position relative to
the floating structure and the other of the auxiliary piston and
the auxiliary cylinder being fixed relative to the earth; and
a conduit providing fluid communication between the auxiliary
variable volume chamber and the secondary cylinder.
21. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system, comprising:
a cylinder having first and second end plates mounted for movement
with the traveling block;
a piston within the cylinder and slidably sealed thereagainst;
a piston rod attached to the piston and extending through and
slidably sealed against the first end plate, the piston rod being
mounted for movement with the load;
the variable chamber formed by the second end plate of the
cylinder, the cylinder, and the piston, being the primary
chamber;
the variable annular chamber between the first end plate of the
cylinder, the cylinder, the piston rod, and the piston, being the
secondary chamber;
means for passively maintaining fluid under pressure in the primary
chamber whereby force is exerted against the piston tending to move
the piston in the direction to support the load;
means for actively introducing fluid into the secondary chamber and
allowing the withdrawal of fluid from the secondary chamber whereby
force is exerted against the piston tending to move the piston in
the direction opposing the support of the load;
transducer means for determining the pressure of the fluid in the
secondary chamber and for generating a first electrical signal
proportional thereto;
transducer means for determining the pressure of the fluid in the
secondary chamber and for generating a second electrical signal
proportional thereto;
adjustable means for generating a third electrical signal
proportional to the selected hook load;
control means operable responsive to the first, second, and third
electrical signals for causing the fluid to be actively introduced
into the secondary chamber and allowing the withdrawal of the fluid
from the secondary chamber.
22. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 21,
including:
pulley means pivotally connected to the end of the piston rod which
extends through the cylinder; and
a cable connected to the cylinder, extending around the pulley, and
connected to the load.
23. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 21,
wherein the means for passively maintaining fluid under pressure in
the primary chamber includes:
a pneumatic accumulator;
a pneumatic-hydraulic interface means in fluid communication with
the pneumatic accumulator; and
means for porviding fluid communication between the
pneumatic-hydraulic interface means and the primary chamber.
24. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 21
wherein the means for actively introducing the fluid into the
secondary chamber and allowing the withdrawal of the fluid from the
secondary chamber includes:
a source of hydraulic fluid;
a variable volume, bi-directional pump in fluid communication with
the source of hydraulic fluid and in fluid communication with the
active chamber; and
control means coupled to the pump for controlling the direction and
the volume of the hydraulic fluid pumped by such pump.
25. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 21,
wherein the means for actively introducing the fluid into the
secondary chamber and allowing the withdrawal of the fluid from the
secondary chamber includes:
an auxiliary piston and cylinder assembly forming an auxiliary
variable volume chamber, one of the auxiliary piston and the
auxiliary cylinder being supported in a fixed position relative to
the floating structure and the other of the auxiliary piston and
the auxiliary cylinder being fixed relative to the earth; and
a conduit providing fluid communication between the auxiliary
variable volume chamber and the secondary chamber.
26. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system, comprising:
a cylinder having first and second end plates mounted for movement
with the traveling block;
a piston within the cylinder and slidably sealed thereagainst;
a piston rod attached to the piston and extending through and
slidably sealed against the first end plate, the piston rod being
mounted for movement with the load;
the variable chamber formed by the second end plate of the
cylinder, the cylinder, and the piston, being the primary
chamber;
the variable chamber between the first end plate of the cylinder,
the cylinder, the piston rod, and the piston, being the secondary
chamber;
means for passively maintaining fluid under pressure in the primary
chamber whereby force is exerted against the piston tending to move
the piston in the direction to support the load;
means for actively introducing fluid into the secondary chamber and
allowing the withdrawal of fluid from the secondary chamber whereby
force is exerted against the piston tending to move the piston in
the direction opposing the supporting of the load;
means associated with the floating structure for determining the
direction and the velocity of the vertical movement of the floating
structure relative to the earth and for generating a first
electrical signal proportional thereto;
means associated with the motion compensation system for
determining the direction and the velocity of the vertical movement
of the load relative to the traveling block and for generating a
second electrical signal proportional thereto;
control means operable responsive to the first and second
electrical signals for causing the fluid to be introduced into the
secondary chamber and allowing the withdrawal of the fluid from the
secondary chamber.
27. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 26,
including:
pulley means pivotally connected to the end of the piston rod which
extends through the cylinder; and
a cable connected to the cylinder, extending around the pulley, and
connected to the load.
28. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 26
wherein the means for passively maintaining fluid under pressure in
the primary chamber includes:
a pneumatic accumulator;
a pneumatic-hydraulic interface means in fluid communication with
the pneumatic accumulator; and
means for providing fluid communication between the
pneumatic-hydraulic interface means and the primary chamber.
29. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 26,
wherein the means for actively introducing the fluid into the
secondary chamber and allowing the withdrawal of the fluid from the
secondary chamber includes:
a source of hydraulic fluid;
a variable volume, bi-directional pump in fluid communication with
the source of hydraulic fluid and in fluid communication with the
active chamber; and
control means coupled to the pump for controlling the direction and
the volume of the hydraulic fluid pumped by such pump.
30. In an earth boring apparatus having a cable operated traveling
block from which is hooked or suspended a load comprising a drill
string or the like with a tool secured thereto, a motion
compensation and/or weight control system according to claim 26,
wherein the means for actively introducing the fluid into the
secondary chamber and allowing the withdrawal of the fluid from the
secondary chamber includes:
an auxiliary piston and cylinder assembly forming an auxiliary
variable volume chamber, one of the auxiliary piston and the
auxiliary cylinder being supported in a fixed position relative to
the floating structure and the other of the auxiliary piston and
the auxiliary cylinder being fixed relative to the earth; and
a conduit providing fluid communication between the auxiliary
variable volume chamber and the secondary chamber.
31. In an earth boring apparatus mounted on a floating structure
and having a drill head or the like supporting a load, an improved
motion compensation and/or weight control system comprising:
a primary piston and cylinder assembly interposed between the
floating structure and the drill head, one of the primary piston
and the primary cylinder being mounted for movement with the
floating structure and the other of the primary piston and the
primary cylinder being mounted for movement with the drill
head;
means for passively maintaining fluid under pressure in the primary
cylinder and on a selected side of the primary piston whereby force
is exerted against the primary piston tending to move the primary
piston longitudinally relative to the primary cylinder in the
direction to support the load;
a secondary piston and cylinder assembly interposed between the
floating structure and the drill head, one of the secondary piston
and the secondary cylinder being mounted for movement with the
floating structure and the other of the secondary piston and the
secondary cylinder being mounted for movement with the drill
head;
means for actively introducing fluid into the secondary cylinder
and onto a selected side of the secondary piston and allowing the
withdrawal of the fluid from the secondary cylinder whereby force
is exerted against the secondary piston tending to move the
secondary piston longitudinally relative to the secondary cylinder
in the direction to oppose the supporting of the load;
means for operatively connecting the primary and secondary pistons
whereby their longitudinal movement is coordinated together;
transducer means for determining the pressure of the fluid in the
primary cylinder and for generating a first electrical signal
proportional thereto;
transducer means for determining the pressure of the fluid in the
secondary cylinder and for generating a second electrical signal
proportional thereto;
adjustable means for generating a third electrical signal
proportional to the selected hook load; and
control means operable responsive to the first, second, and third
electrical signals for causing the fluid to be introduced into the
secondary cylinder and allowing the fluid to be withdrawn from the
secondary chamber.
32. In an earth boring apparatus mounted on a floating structure
and having a drill head or the like supporting a load, an improved
motion compensation and/or weight control system comprising:
a primary piston and cylinder assembly interposed between the
floating structure and the drill head, one of the primary piston
and the primary cylinder being mounted for movement with the
floating structure and the other of the primary piston and the
primary cylinder being mounted for movement with the drill
head;
means for passively maintaining fluid under pressure in the primary
cylinder and on a selected side of the primary piston whereby force
is exerted against the primary piston tending to move the primary
piston longitudinally relative to the primary cylinder in the
direction to support the load;
a secondary piston and cylinder assembly interposed between the
floating structure and the drill head, one of the secondary piston
and the secondary cylinder being mounted for movement with the
floating structure and the other of the secondary piston and the
secondary cylinder being mounted for movement with the drill
head;
means for actively introducing fluid into the secondary cylinder
and onto a selected side of the secondary piston and allowing the
withdrawal of the fluid from the secondary cylinder whereby force
is exerted against the secondary piston tending to move the
secondary piston longitudinally relative to the secondary cylinder
in the direction to oppose the supporting of the load;
means for operatively connecting the primary and secondary pistons
whereby their longitudinal movement is coordinated together;
means associated with the floating structure for determining the
direction and the velocity of the vertical movement of the floating
structure relative to the earth and for generating a first
electrical signal proportional thereto;
means associated with the motion compensation system for
determining the direction and the velocity of the vertical movement
of the drill head relative to the floating structure and for
generating a second electrical signal proportional thereto; and
control means operable responsive to the first and second
electrical signals for causing the fluid to be actively introduced
into the secondary cylinder and allowing the withdrawal of the
fluid from the secondary cylinder.
33. In a load supporting assembly mounted on a floating structure
for supporting a load movable vertically relative to the floating
structure, a motion compensation and/or weight control system,
including:
an expansible and contractible mechanism secured between the
floating structure and the load;
means for determining the velocity of the vertical movement of the
floating structure relative to the earth and generating a first
electrical signal proportional thereto;
means for determining the velocity of the expansion and contraction
of the expansible and contractible mechanism and generating a
second electrical signal proportional thereto;
means for determining the vertical position of the floating
structure relative to the earth and generating a third electrical
signal proportional thereto;
means for determining the magnitude of expansion and contraction of
the expansible and contractible mechanism and generating a fourth
electrical signal proportional thereto;
means for actively supplying fluid to the expansible and
contractible mechanism and allowing the withdrawal of the fluid
from the expansible and contractible mechanism to cause it to
expand and contract; and
control means operable responsive to the first, second, third and
fourth electrical signals for controlling the operation of the
means for actively supplying the fluid and allowing the withdrawal
of the fluid, the control means including means operable responsive
to the first, second, third and fourth electrical signals for
generating a fifth electrical signal proportional to Q in the
following equation:
Q = k.sub.1 (Vs) + k.sub.2 (Ve) + k.sub.3 (Le).
34. In a load supporting assembly mounted on a floating structure
for supporting a load movable vertically relative to the floating
structure, a motion compensation and/or weight control system
according to claim 33, wherein the means for actively supplying
fluid into the expansible and contractible mechanism and allowing
the withdrawal of the fluid from the expansible and contractible
mechanism includes:
a bi-directional, variable volume pump;
a source of hydraulic fluid;
means establishing fluid communication between the source of fluid
and the pump and between the pump and the expansible and
contractible mechanism; and
a servo valve coupled to the output of the control means and
operable responsive to the fifth electrical signal for controlling
the pump.
35. In a load-supporting assembly which is mounted on a floating
structure, which load-supporting assembly supports a load movable
vertically with respect to the floating structure and which
load-supporting assembly includes a motion compensation and/or
weight control system associated therewith, the system including a
primary piston and cylinder assembly mounted between the
load-supporting assembly and the load for generating forces tending
to lift the load and a secondary piston and cylinder assembly
mounted betwen the load-supporting assembly and the load for
generating forces tending to oppose the lifting of the load and
having the primary and secondary pistons operatively connected to
each other for coordinated movement, the method of compensating for
the movement of the floating structure, including the steps of:
passively supplying fluid under pressure into the primary cylinder
and against the primary piston whereby each of the primary and
secondary pistons is moved longitudinally within its cylinder a
selected distance in the direction to lift the load and the system
thereby lifts the load;
actively supplying hydraulic fluid into the secondary cylinder and
against the secondary piston whereby each of the secondary and
primary pistons is moved longitudinally within its cylinder a
selected distance in the direction opposite to that for lifting the
load and the system thereby lowers the load; and, thereafter,
actively supplying hydraulic fluid into and allowing the withdrawal
of hydraulic fluid out of the secondary cylinder responsive to data
indicative of the vertical movement of the floating structure
relative to the earth, the magnitude of the expansion and
contraction of the piston and cylinder assemblies, the velocity of
the vertical movement of the floating structure relative to the
earth, and the velocity of the expansion and contraction of the
piston and cylinder assemblies, whereby the piston and cylinder
assemblies expand and contract to compensate for the movement of
the floating structure.
36. In a load-supporting assembly which is mounted on a floating
structure, hich load-supporting assembly supports a load movable
vertically with respect to the floating structure and which
load-supporting assembly includes a motion compensation and/or
weight control system associated therewith, the system including a
primary piston and cylinder assembly mounted between the
load-supporting assembly and the load for generating forces tending
to lift the load and a secondary piston and cylinder assembly
mounted between the load-supporting assembly and the load for
generating forces tending to oppose the lifting of the load and
having the primary and secondary pistons operatively connected to
each other for coordinated movement, the method of compensating for
the movement of the floating structure, including the steps of:
passively supplying fluid under pressure into the primary cylinder
and against the primary piston whereby each of the primary and
secondary pistons is moved longitudinally within its cylinder and a
selected distance in the direction to lift the load and the system
thereby lifts the load;
actively supplying hydraulic fluid into the secondary cylinder and
against the secondary piston whereby each of the secondary and
primary pistons is moved longitudinally within its cylinder a
selected distance in the direction opposite to that for lifting the
load and the system thereby lowers the load; and, thereafter,
actively supplying hydraulic fluid into and allowing the withdrawal
of hydraulic fluid out of the secondary cylinder responsive to data
indicative of the vertical movement of the floating structure
relative to the earth, the magnitude of the expansion and
contraction of the piston and cylinder assemblies, the velocity of
the vertical movement of the floating structure relative to the
earth, and the velocity of the expansion and contraction of the
piston and cylinder assemblies, whereby the piston and cylinder
assemblies expand and contract to compensate for the movement of
the floating structure;
such step of actively supplying hydraulic fluid into and allowing
the withdrawal of hydraulic fluid out of the secondary cylinder
including solving the equation:
Q = k.sub.1 (Vs) + k.sub.2 (Ve) + k.sub.3 (Le).
37. In a load-supporting assembly which is mounted on a floating
structure, which load-supporting assembly supports a load movable
vertically with respect to the floating structure and which
load-supporting assembly includes a motion compensation and/or
weight control system associated therewith, the system including a
primary piston and cylinder assembly mounted between the
load-supporting assembly and the load for generating forces tending
to lift the load and a secondary piston and cylinder assembly
mounted between the load-supporting assembly and the load for
generating forces tending to oppose the lifting of the load and
having the primary and secondary pistons operatively connected to
each other for coordinated movement, the method of compensating for
the movement of the floating structure and/or the movement of the
load into the earth whereby a substantially constant pressure is
maintained between the load and the earth, including the steps
of:
passively supplying fluid under pressure into the primary cylinder
and against the primary piston whereby each of the primary and
secondary pistons is moved longitudinally within its cylinder a
selected distance in the direction to lift the load and the system
thereby lifts the load;
actively supplying hydraulic fluid into the secondary cylinder and
against the secondary piston whereby each of the secondary and
primary pistons is moved longitudinally within its cylinder a
selected distance in the direction opposite to that for lifting the
load and the system thereby lowers the load;
lowering at least the portion of the system comprising the primary
and secondary piston and cylinder assemblies and the load mounted
therefrom until the load is in contact with the earth and a
selected pressure exists between the load and the earth; and,
thereafter,
actively supplying hydraulic fluid into and allowing the withdrawal
of hydraulic fluid out of the secondary cylinder responsive to data
indicative of the pressure of the fluid in the primary cylinder and
the pressure of the hydraulic fluid in the secondary cylinder,
whereby the piston and cylinder assemblies expand and contract to
compensate for the movement of the floating structure relative to
the earth and/or the movement of the load into the earth.
38. In a load-supporting assembly which is mounted on a floating
structure, which load-supporting assembly supports a load movable
vertically with respect to the floating structure and which
load-supporting assembly includes a motion compensation and/or
weight control system associated therewith, the system including a
primary piston and cylinder assembly mounted between the
load-supporting assembly and the load for generating forces tending
to lift the load and a secondary piston and cylinder assembly
mounted between the load-supporting assembly and the load for
generating forces tending to oppose the lifting of the load and
having the primary and secondary pistons operatively connected to
each other for coordinated movement, the method of compensating for
the movement of the floating structure and/or the movement of the
load into the earth whereby a substantially constant pressure is
maintained between the load and the earth, according to claim 37,
wherein the step of actively supplying hydraulic fluid into and
allowing the withdrawal of hydraulic fluid out of the secondary
cylinder includes the step of solving the following equation:
Q = (P.sub.1 A.sub.1 - P.sub.2 A.sub.2) - k
Description
BACKGROUND OF THE INVENTION
This invention relates to a motion compensation and/or weight
control system for an assembly that supports a load. This invention
has particular application to a load-supporting assembly, such as
an earth-boring assembly, mounted on a floating structure.
In the use of conventional earth-boring assemblies, it is often
desirable to maintain a constant weight on a tool being used to
bore into the earth. Numerous so-called "automatic driller"
apparatus have been developed in an attempt to solve this problem.
This constant weight problem is intensified when the hole being
bored in the earth is under water and the earth-boring assembly is
mounted on a floating structure. As the structure moves upwardly
and downwardly with the waves, the weight applied to the tool
through the drill string or the like is alternately decreased
(sometimes to the extent of lifting the tool from contact with the
earth) and increased (sometimes to the extent of damaging the tool
or the drill string).
Other problems encountered in utilizing an earth-boring assembly or
other load-supporting assembly mounted on a floating structure are
to maintain the tool or load suspended on a drill string or the
like at a constant location and to move the tool or load upwardly
or downwardly at selected velocities. For example, it is often
desirable to maintain a cutting tool inside a well casing at a
constant location intermediate its length. And it is often
desirable to land smoothly a blowout preventer apparatus on a
subsurface wellhead. However, the upward and downward movement of
the floating structure supporting the earth-boring assembly may
cause the cutting tool to move about vertically inside the well
casing or cause the blowout preventer to slam into the
wellhead.
Various attempts have been made to stabilize a floating structure
supporting an earth-boring assembly, such as are exemplified in the
U.S. Pat. No. 3,490.406. Various attempts have been made to develop
slip joints or compensator means in the drill string or conductor
itself, such as are exemplified in the U.S. Pat. No. 3,353,851 and
No. 3,319,981.
Additionally, various attempts have been made to develop a motion
compensation or weight control system to be secured between the
load and the assembly supporting the load. Illustrative of such
efforts are the following U.S. Pat. Nos.: 3,804,183; 3,793,835;
3,721,293; 3,718,316; 3,714,995; Re. 27,261; 3,469,820; 3,309,065;
3,285,574; 3,259,371; 3,158,208; 3,158,206; 3,151,686; 2,945,677;
and 2,945,676. For one reason or another, each of the prior motion
compensation systems is disadvantageous or undesirable.
Prior efforts to construct a motion compensation and/or weight
control system to be mounted between the supporting assembly and
its load have recognized the need for some sort of expansible and
contractible mechanism which is capable of generating uniform
forces at any point of its expansion and contraction range.
Generally, a sturdy, telescoping, piston and cylinder assembly has
been chosen to provide the expansible and contractible movement.
However, great difficulty has been experienced in constructing a
practical motion compensation and/or weight control system wherein
the piston and cylinder assembly provides uniform forces throughout
its entire movement range.
Numerous of such prior systems have attempted to operate a piston
and cylinder assembly so that it generates uniform forces
throughout its movement range by supplying fluid at a predetermined
pressure to the piston and cylinder assembly. This contained fluid
generally is a gas alone or a hydraulic-pneumatic combination in
which a gas is maintained in an accumulator bank at a predetermined
pressure and the pressure of the gas is transferred to a hydraulic
fluid which in turn is supplied to the piston and cylinder
assembly. These systems for controlling the movement of the piston
and cylinder assembly are commonly referred to as "passive" systems
because there is no pump or the like actively forcing fluid into
the piston and cylinder assembly.
Unfortunately, no practical passive system has been constructed
which will provide true motion compensation and/or weight control.
This is because the volume of the contained gas changes as the gas
or the hydraulic fluid in the pneumatic-hydraulic combination moves
in and out of the piston and cylinder assembly responsive to the
longitudinal movement of the piston. In accordance with Charles'
law (assuming the temperature of the fluid is relatively constant),
this change in the volume of the contained gas produces a change in
its pressure. And this change in the pressure of the gas results in
a corresponding change in the pressure of the hydraulic fluid in
the piston and cylinder assembly, which in turn produces erroneous
motion compensation and/or weight control.
Of course, the magnitude of this pressure variation can be
decreased by increasing the volume of the accumulator bank
containing the pressurized gas. But this has practical limitations.
Indeed, even the largest practical accumulator system being
utilized today to control passively a heavy-duty motion
compensation and/or weight control system, still produces
approximately a plus or minus four percent pressure error as the
piston moves throughout its stroke. And it is not uncommon in the
smaller passively operated systems for the pressure error to
increase up to approximately plus or minus eight percent. Moreover,
the friction of the fluid moving into and out of the cylinder and
its attendant components, the friction of the packing between the
piston and the cylinder, and the inertia of the piston, cause
additional pressure losses. These combined pressure losses in a
passively operated system can easily equal approximately plus or
minus ten percent.
Other such prior systems have attempted to provide accurate motion
compensation and/or weight control by affirmatively pumping or
otherwise forcing hydraulic fluid into and regulating its flow out
of the piston and cylinder assembly to maintain a constant pressure
in the cylinder at all times irrespective of the longitudinal
position of the piston within the cylinder. These systems are
commonly called "active" systems. However, these active systems
have practical drawbacks. Motion compensation and/or weight control
systems to be used to support heavy loads are quite massive. It is
not uncommon for there to be two cylinders, each of which is in
excess of 20 feet in length and in excess of 100 square inches in
cross-sectional area. As the piston moves longitudinally within the
cylinder, a vast amount of hydraulic fluid must move in and out of
the cylinder. To actively move such hydraulic fluid into and out of
a cylinder requires enormous horsepower and, accordingly, very
large pumps. It has been found that it is simply not practical to
construct a purely active motion compensation and/or weight control
system for large magnitude loads.
U.S. Pat. No. 3,259,371 to Goepfert et al discloses a motion
compensation system for use with a load-supporting assembly mounted
on a floating structure which is a combination passive and active
system. The Goepfert motion compensation system includes a linear
positioning device or expansible and contractible mechanism which
has coupled to one end thereof a source of constant pressure fluid
and which has coupled to the other end thereof a hydraulic control
valve connected to a pump and to a source of hydraulic fluid. The
control valve is operated by electrical signals generated by a
controller responsive to the linear position of the floating
structure relative to the earth and the linear position of the
linear positioning device relative to its activator rod.
Prior art motion compensation and/or weight control systems usually
have operated either in a pressure mode, that is, responsive to
changes in the pressure of the fluid in the expansible and
contractible mechanism, or in a position mode, that is, responsive
to the expansion and contraction of the expansible and contractible
mechanism and the movement of the floating structure relative to
the earth. Depending upon the task to be accomplished, there are
certain advantages attendant to operating either in the pressure
mode or the position mode. Most of the prior art motion
compensation and/or weight control systems cannot be readily
switched between the pressure mode and the position mode.
Additionally, those prior art motion compensation and/or weight
control systems which are capable of operating in the position mode
function responsive to input data indicative only of the magnitude
and direction of the expansion and contraction of the expansible
and contractible mechanism and of the movement of the floating
structure relative to the earth.
OBJECTS OF THE INVENTION
The improved motion compensation and/or weight control system
according to this invention is a combination passive and active
system which overcomes the disadvantages of the purely passive
systems and the purely active systems, and is an improvement over
the combination passive and active system disclosed in Goepfert et
al U.S. Pat. No. 3,259,371.
The improved motion compensation and/or weight control system
according to this invention may be generally described as a system
mounted on a load-supporting assembly for supporting a load which
is movable relative to the load-supporting assembly. The system
includes an improved expansible and contractible mechanism which
preferably depends from a traveling block, drill head or the like
mounted in a derrick, tower or the like. The load to be supported
then depends from the improved expansible and contractible
mechanism. The improved expansible and contractible mechanism
according to this invention includes at least one primary piston
and cylinder assembly, preferably passively operated, providing
forces at least sufficient to support the load. The improved
expansible and contractible mechanism also includes at least one
secondary piston and cylinder assembly, preferably actively
operated, providing forces opposing the forces of the primary
piston and cylinder assembly.
The motion compensation and/or weight control system according to
this invention can be operated in either the pressure mode or the
position mode. When the system is operated in the position mode,
hydraulic fluid is actively supplied to and withdrawn from the
secondary piston and cylinder assembly responsive not only to the
magnitude and direction of the expansion and contraction of the
expansible and contractible mechanism and of the movement of the
floating structure relative to the earth, but also to the velocity
of such expansion and contraction and such movement.
It is an object, therefore, of this invention to provide an
improved motion compensation and/or weight control system which
overcomes the disadvantages and undesirable characteristics of
prior motion compensation and/or weight control systems.
It is an object of this invention to provide an improved motion
compensation and/or weight control system for a load-supporting
assembly mounted on a floating structure, which system is more
accurate than prior systems in compensating for the movement of the
floating structure and/or in maintaining a constant weight on a
tool supported by the load-supporting device.
It is an object of this invention to provide an improved motion
compensation and/or weight control system for a load-supporting
assembly which, when used with a cable and a traveling block,
provides an expansible and contractible mechanism between the
traveling block and the load and thus reduces the length of the
piston stroke required by prior systems having an expansible and
contractible mechanism secured to the cable in the dead-end
thereof.
It is an object of this invention to provide an improved motion
compensation and/or weight control system which includes an
improved expansible and contractible mechanism comprising a
passively operated piston and cylinder assembly providing forces
supporting the load and an opposing actively operating piston and
cylinder assembly providing biasing forces.
It is an object of this invention to provide an improved motion
compensation and/or weight control system which can be operated
either in a position mode or a pressure mode.
It is an object of this invention to provide an improved motion
compensation and/or weight control system which, when operated in
the position mode, functions responsive not only to input data
indicative of the direction and magnitude of the expansion and
contraction of the expansible and contractible mechanism and of the
movement of the floating structure relative to the earth, but also
responsive to input data indicative of the velocity of such
expansion and contraction and such movement.
It is an object of this invention to provide an improved motion
compensation and/or weight control system for use with a block and
cable earth-boring assembly, which system employs an expansible and
contractible mechanism which may be easily removed from active use
in the earth-boring assembly during tripping.
This invention possesses many other advantages and has other
objects which may be made more clearly apparent from the
consideration of the forms in which it may be embodied. Several
embodiments of the invention are shown in the drawings accompanying
and forming part of the present specification. These embodiments of
the invention will now be described in detail for the purpose of
illustrating the general principles of the invention; but it is to
be understood that such detailed descriptions are not to be taken
in a limiting sense.
BRIEF DESCRIPTION OF THE DRAWINGS
Referring to the drawings in which like numerals represent like
parts:
FIG. 1 is a diagramatic view of an embodiment of a motion
compensation and/or weight control system according to this
invention in association with an earth-boring assembly mounted on a
floating structure for drilling a well hole beneath a body of
water.
FIG. 2 is a front elevational view, with certain parts shown in
longitudinal section of the expansible and contractible mechanism
of the system disclosed in FIG. 1 in a partially telescoped
position, and with the components of the system for passively
supplying hydraulic fluid and for actively supplying hydraulic
fluid to the expansible and contractible mechanism being shown
schematically.
FIG. 3 is a graph depicting with respect to time the typical
vertical movement of a floating drilling rig and the typical
vertical movement of the piston rod of the expansible and
contractible mechanism relative to its outer cylinder.
FIG. 4 is a schematic and block diagram of a preferred arrangement
of the electrical components of the control means in the active
portion of the system.
FIG. 5 is a front elevational view, with certain parts shown in
longitudinal section, of an alternate component for actively
supplying hydraulic fluid to the expansible and contractible
mechanism disclosed in FIG. 2.
FIG. 6 is a front elevational view, with certain parts shown in
longitudinal section, of an alternate expansible and contractible
mechanism according to this invention.
FIG. 7 is a diagrammatic view of an alternate embodiment of the
motion compensation and/or weight control system according to this
invention in association with an earth-boring apparatus having a
hydraulically supported drill head and mounted on a floating
structure.
FIG. 8 is a front elevational view, with certain parts shown in
longitudinal section, of still another embodiment of an expansible
and contractible mechanism according to this invention.
FIG. 9 is a front elevational view, with certain parts shown in
longitudinal section, of still another embodiment of an expansible
and contractible mechanism according to this invention.
FIG. 10 is a front elevation view, with certain parts shown in
longitudinal section, of still another embodiment of an expansible
and contractible mechanism according to this invention, with the
attendant component for passively supplying hydraulic fluid thereto
shown schematically.
DESCRIPTION OF PREFERRED EMBODIMENTS OF INVENTION
A. motion compensation and/or weight control system utilized with a
floating, block and cable, earth-boring assembly
1. Schematic description of earth-boring assembly and system
FIG. 1 illustrates a preferred embodiment of the motion
compensation and/or weight control system according to this
invention utilized in connection with an earth-boring assembly
having cables and a traveling block and mounted on a structure
floating in water. The earth-boring assembly is illustrated
drilling a vertical well hole 11 into a sub-aqueous seabed 12. The
floating structure 13 is suitably anchored (not shown) against
excessive lateral displacement for the purpose of holding the drill
string 14 in centered relation with respect to the well hole. A
drill bit 15 is secured to the lower end of the drill string 14 and
is in contact with the earth. A marine riser 16 extends from the
wellhead 17 at the sea floor upwardly to a location adjacent the
floating structure 13.
The upper portion of the drill string 14 is secured to a kelly 18
passing through a rotary table 19. The upper end of the kelly is
secured to a swivel 20 which is in turn suspended from a hook 21
connected to the lower portion of the expansible and contractible
mechanism 22 of the improved motion compensating and/or weight
control system according to this invention. A mud line 23 is
connected to the swivel.
The earth-boring assembly illustrated in FIG. 1 employs a derrick
24 having a crown block 25 secured at the top thereof. Depending by
cable 26 from the crown block 25 is traveling block 27. Cable 26 is
dead-ended to the floating structure 13 at a selected point 28,
extended upwardly and suitably reeved about crown block 25 and
traveling block 27, then extended downwardly to the drawworks 29.
The drawworks 29 winds-in or winds-out the cable 26 to raise and
lower the traveling block 27. A weight indicator 30 preferably is
coupled into the cable 26 at a selected location, such as adjacent
the dead-end thereof.
The motion compensation and/or weight control system according to
this invention utilizes an expansible and contractible mechanism 22
to provide a desired telescoping action whereby selected movement
of the load relative to the floating structure can be effected or,
if the load is in contact with the earth, a certain pressure can be
maintained between the load and the earth. The expansible and
contractible mechanism 22 of the motion compensating and/or weight
control system according to this invention is shown in FIG. 1
secured or interposed between traveling block 27 and hook 21. Thus,
the load--comprising swivel 20, kelly 18, drill string 14, drill
bit 15, and other attendant apparatus secured thereto--is supported
directly by the expansible and contractible mechanism of the motion
compensation and weight mechanism 22. The weight of the load hooked
to or supported by the expansible and contractible mechanism 22 is
referred to as the "hook load." By locating the expansible and
contractible mechanism 22 between the traveling block and the load,
rather than between the dead-end of cable 26 and the floating
structure 13, the required amount of expansion and contraction of
the mechanism 22 is reduced. For example, assuming that the crown
block and traveling block provided a ten to one reduction in the
movement of the cable 26, an expansible and contractible mechanism
mounted between the floating structure 13 and the dead-end of the
cable 26 would have to expand and contract a distance of forty feet
to move the load four feet. Additionally, an expansible and
contractible mechanism mounted above the crown block or on the
floating structure must contend with the friction forces generated
by the reversal of the crown block and the traveling block as the
cable is reeved in and out during the compensation cycle.
Mounted on the floating structure 13 is an oil/air interface tank
35, a bank 36 of air accumulator tanks, and a means 37 for actively
supplying hydraulic fluid. As will hereafter be explained, the
oil/air interface tank 35 and the bank 36 of air accumulator tanks
function to passively introduce and withdraw hydraulic fluid to and
from the expansible and contractible mechanism 22 and means 37
functions to actively introduce and withdraw hydraulic fluid to and
from the expansible and contractible mechanism 22. Also mounted on
the floating structure is a rotatable drum 38 which, as will be
hereinafter explained, is employed in determining the vertical
position of the floating structure with respect to the seabed.
As illustrated in FIG. 2, a preferred embodiment of the expansible
and contractible mechanism 22 according to this invention comprises
two identical piston and cylinder assemblies 39 and 39'. Each of
the piston and cylinder assemblies 39 and 39' is secured to a
support member 40, which in turn is secured to the traveling block
27. Movable longitudinally within each of the cylinders 39 and 39'
is a piston rod 41 and 41', respectively. Piston rods 41 and 41'
are secured to a second support member 42, from which depends the
hook 21.
In this embodiment of the motion compensation and/or weight control
system according to this invention, each of the two piston and
cylinder assemblies of the expansible and contractible mechanism 22
extends upwardly along the side of the traveling block. For a
selected size of expansible and contractible mechanism, this
reduces the height beneath the derrick of the total mechanism.
However, the expansible and contractible mechanism of the improved
motion compensation and/or weight control system according to this
invention is not limited to a piston and cylinder assembly secured
to either side of the traveling block. Indeed, it can comprise more
than two cylinder and piston assemblies surrounding a traveling
block, one cylinder and piston assembly depending from the
traveling block (as hereinafter described), or other configurations
(some of which are hereinafter described).
Each of the piston and cylinder assemblies 39 and 39' (only piston
and cylinder assembly 39 will be described fully hereinafter) in
this embodiment of this invention comprises an outer, primary
cylinder 43 having end plates 44 and 45. Attached to the upper end
plate 44 of outer cylinder 43 and depending therefrom is an inner
cylinder 46 disposed concentrically within the outer cylinder 43.
Inner cylinder 46 preferably extends the full length of outer
cylinder 43 and protrudes a slight distance beyond the lower end
plate 45 of outer cylinder 43. The piston rod 41 previously
referred to is cylindrical and hollow, and is slidably disposed
around the inner cylinder 46. A first piston 47 is secured to the
upper end of the piston rod 41 within the annular chamber formed
between the inner cylinder 46 and the outer cylinder 43. The first
piston 47 is slidable in such annular chamber and carries a
suitable seal ring 48 for slidably sealing against the outer
cylinder wall. The inner cylinder 46 carries a suitable seal ring
49 for slidably sealing against the slidable piston rod 41. The
lower end of the piston rod 41 comprises a second piston 50.
The annular chamber formed between the lower end plate 45, outer
cylinder 43, piston rod 41, and first piston 47 comprises a primary
chamber 51, sometimes referred to as the passive chamber. The
chamber formed within the upper end plate 44, inner cylinder 46,
hollow piston rod 41, and the second piston 50 comprises a
secondary chamber 52, sometimes referred to as the active chamber.
The annular chamber formed between the upper end plate 44, first
piston 47, and inner cylinder 46 comprises a deceleration chamber
53.
A port 54 is provided in the lower part of outer cylinder 43 in
fluid communication with passive chamber 51. A conduit 55 provides
fluid communication from the port 54 to the oil/air interface tank
35. The oil/air interface tank 35 is in fluid communication through
conduit 56 with the bank 36 of air accumulator tanks. Thus, the
bank of air accumulator tanks and the oil/air interface tank
provide the standard pneumatic/hydraulic system for passively
supplying and receiving pressurized hydraulic fluid to and from the
primary chamber 51. In fluid communication with the hydraulic fluid
in primary chamber 51 is a pressure transducer 57 which determines
the pressure of the hydraulic fluid and generates an electrical
signal proportional thereto.
A port 58 is provided through the upper end plates and into each of
the secondary or active chambers 52 and 52'. A conduit 59 places
active chambers 52 and 52' in fluid communication with a means 37
for introducing and withdrawing hydraulic fluid into and from
active chambers 52 and 52'. A pressure transducer 60 such as a Tyco
Instruments Model AF 3000, is in communication with the active
hydraulic fluid being supplied to active chambers 52 and 52'. Such
pressure transducer determines the pressure of the fluid in the
active chambers and generates a signal proportional thereto.
A preferred means for actively introducing and withdrawing
hydraulic fluid into and from secondary chambers 52 and 52' is
illustrated within the dashed lines 37 in FIG. 2. Conduit 59 is in
fluid communication with a pump 61. Pump 61 is in fluid
communication through conduit 62 with a sump 63 in which hydraulic
fluid is maintained. Pump 61 may be any of various commercially
available devices, but preferably is a variable volume,
bidirectional, over-center pump such as manufactured by Von Roll,
Ltd. of Switzerland, Rex Roth, Sunstrand, or Dynapower. In the
preferred pump, the direction in which hydraulic fluid is pumped
and the volume of hydraulic fluid so pumped is controlled by the
position of the yoke of the pump. The position of the yoke of the
pump is controlled by a servo value 64 such as is well known to
those skilled in the art. The operation of the servo value is
controlled by electrical signals supplied thereto from control
means 65. Control means 65 operates, as will hereafter be
explained, responsive to a feedback signal from servo valve 64 and
input signals supplied to the control means 65 which vary depending
upon whether the system is operated in the tied-to-ground mode or
the pressure mode.
Other types of pumps and arrangements of servo values may be
utilized rather than the variable-volume, bidirectional pump. For
example, Goepfert et al U.S. Pat. No. 3,259,371 discloses a
unidirectional pump coupled to a servo valve which varies the
direction of flow of the drilling fluid back and forth between a
cylinder and a sump.
As illustrated in FIG. 2, in each of the piston and cylinder
assemblies there is an annular chamber 53 between the upper end
plate 44 of the outer cylinder 43, the inner cylinder 46, and the
first piston 47. This annular chamber 53 is a deceleration chamber.
It preferably contains a selected amount of hydraulic fluid. The
upper end plate 44 of outer cylinder 43 preferably has inclined
shoulders 66 providing a tapered, truncated surface leading to one
or more orifices 67 which communicate with an exterior chamber 68.
In the case of a sudden upward movement of piston rod 41, such as
may be caused by the parting of the load secured to hook 21, the
hydraulic fluid contained in deceleration chamber 53 will slow the
upward movement of the first piston 47 as the fluid flows through
the restrictive orifices 67 into the exterior chamber 68.
Additionally, as will be hereinafter explained, the hydraulic fluid
contained in the active chamber 52 will oppose the upward movement
of piston rod 41 and thus aid in the deceleration.
FIG. 3 illustrates graphically with respect to time the typical
vertical movement of the floating structure 13 relative to the
wellhead 17. The vertical movement of the floating structure
responsive to normal wave motion produces a graph 71 which is
sinusoidal. The floating structure 13 is farthest from the wellhead
17 at point in time 72 when it is on the crest of the wave and is
closest to the wellhead 17 at point in time 73 when it is in the
trough of the wave. As shown in FIG. 3, the floating structure is
experiencing twelve foot heaves, that is, plus and minus six feet
from the center position of the heave. As the floating structure 13
moves, the outer cylinders 43 and 43' of the expansible and
contractible mechanism 22 will likewise move (assuming the
drawworks 29 is locked). In order to obtain proper motion
compensation and/or weight control of the load, the piston rods 41
and 41' should move relative to the outer cylinders 43 and 43' as
the floating structure heaves. When the system is operated such
that the load remains stationary vertically with respect to the
earth, the piston rods 41 and 41' should move relative to the outer
cylinders 43 and 43' in the direction opposite to the floating
structure at a distance and at a velocity equal to the movement of
the floating structure, as illustrated by the dashed sinusoidal
line 74. However, as will become apparent hereinafter, when the
system is operated such that a selected weight is maintained on a
tool in contact with the earth, the movement of the piston rods
relative to the outer cylinders will not necessarily "track" the
movement of the floating structure.
As will be hereinafter explained, the various sensors utilized to
produce input data for the control means 65 will vary depending
upon the mode in which the system is operated. The pressure
transducers 57 and 60 previously described constitute one set of
sensors for generating input signals. The other set of sensors
comprises means for determining the position of the piston rods 41
and 41' relative to the outer cylinders 43 and 43', means for
determining the velocity of the movement of the piston rods 41 and
41' relative to the outer cylinders 43 and 43', means for
determining the position of the floating structure 13 relative to
the wellhead 17, and means for determining the velocity of the
movement of the floating structure 13 relative to the wellhead 17.
These means may be of numerous devices well known to those skilled
in the art. However, as illustrated in FIG. 2, the means for
determining the position of the piston rods relative to the outer
cylinders preferably comprises a position transducer 75 secured
between the first support member 40 and the second support member
42. The position transducer 75, such as a Beckman potentiometer, a
Bourns potentiometer, or a Lockheed Electronics position
transducer, preferably comprises a spring-loaded rotary element 76
secured to the first support member and a line or cable 77 secured
to the second support member 42. Linear movement of the second
support member 42 relative to the first support member 40 causes
the cable 77 to wind onto and unwind from the rotary element 76,
thereby rotating the rotary element. The position transducer 75
generates an electrical signal proportional to the direction and
magnitude of the rotation of the rotary element, which electrical
signal is coupled via a conductor (not shown) to the control means
65. The means for determining the direction and the velocity of the
movement of the piston rods relative to the outer cylinders
preferably comprises a velocity transducer 78, such as a Servotek
DC Tachometer or other commercially available device, also secured
between the first and second support members. Preferably the
velocity transducer 78 comprises a spring-loaded rotary member
secured to the first support member and a line or cable secured to
the second support member. Linear movement of the two support
members relative to each other causes the cable to wind onto and
unwind from the rotary element. The velocity transducer 78
generates an electrical signal proportional to the direction and
velocity of the rotation of the rotary element, which electrical
signal is coupled to the control means 65 via conductor (not
shown).
There are many devices well known to those skilled in the art which
may be used to monitor the vertical position of the floating
structure relative to the wellhead. Dynamically positioned vessels
are being constructed today in which sonar, accelerometers, lasers,
and other sophisticated electronics are utilized to monitor the
position of the vessel and to generate data proportional thereto.
The means for determining the linear position of the floating
structure relative to the wellhead preferably comprises, as
illustrated in FIG. 1, a cable 79 secured to the marine riser 20,
which in turn is secured to the wellhead on the sea floor.
Alternately, the cable 79 could be connected to the guidelines or
directly to the wellhead. The cable 79 is reeved around the
rotatable drum 38. Drum 38 maintains a constant tension on the
cable 79 and winds or unwinds the cable responsive to the movement
of the floating structure 13 relative to the wellhead. A position
transducer 80, such as previously described with respect to
position transducer 75 or one of the numerous shaft encoders
manufactured by Astrosystems, Inc. and well known in the art, is
attached to drum 38. The position transducer produces an electrical
signal proportional to the direction and magnitude of the rotation
of such drum 38, which signal is coupled to the control means 65
via conductor (not shown). The means for determining the direction
and the velocity of the movement of the floating structure relative
to the wellhead preferably comprises a rotatable velocity
transducer 81, such as is well known to those skilled in the art,
attached to drum 38. The velocity transducer 81 produces an
electrical signal proportional to the direction and velocity of
rotation of the drum 38, which signal is coupled to the control
means 65 via conductor (not shown).
An optional sensor means comprises another position indicating
device (not shown) associated with the draw works 29 or with the
crown block 25 for indicating the amount of cable 26 wound-in or
wound-out by the draw works 29. Such position indicating device
generates an electrical signal proportional to the length of the
cable 26 wound-in or wound-out from the draw works, which signal
may be utilized to determine the position of the traveling block 27
relative to the floating structure 13. A typical position
transducer would be the Beckman potentiometer, Bourns
potentiometer, or Lockheed Electronics position transducers.
When the improved motion compensation and/or weight control system
according to this invention illustrated in FIGS. 1 and 2 is
operated in the position mode, the control means 65 functions
responsive to the electrical signals generated by position
transducer 75, velocity transducer 78, position transducer 80, and
velocity transducer 81, to cause servo valve 64 to operate pump 61
such that hydraulic fluid is supplied to and withdrawn from the
active chambers 52 and 52'.
At first, it was believed that in the position mode, effective
motion compensation and/or weight control could be accomplished if
the control means 65 functioned responsive to only the electrical
signals generated by position transducer 75 and the position
transducer 80. However, it was determined empirically that, in the
position mode, the system operated better if the control means was
provided additional input data. For example, as illustrated in FIG.
3, if at point in time 82 the electrical signals from position
transducers 75 and 80 inform control means 65 that sufficient
hydraulic fluid has been withdrawn from the active chambers 52 and
52' to compensate for the error in the passive portion of the
system as the floating structure 13 moves downwardly, then the
control means 65 will cause the servo valve to operate pump 61 such
that at point in time 82 no additional hydraulic fluid is either
withdrawn from or supplied to the active chambers 52 and 52'.
Thereafter, as the floating structure 13 moves further downward,
such as at point in time 83, additional hydraulic fluid must be
withdrawn from the active chambers 52 and 52' to compensate for the
additional error in the passive portion of the system. However,
since no hydraulic fluid was being withdrawn from the active
chambers 52 and 52' at point in time 83, error in the motion
compensation and/or weight control will result during the time
interval between point in time 82 and the point in time that the
proper amount of hydraulic fluid is withdrawn from the active
chambers 52 and 52'. And then the control means 65 will cause servo
valve 64 to operate pump 61 such that an excess of hydraulic fluid
is withdrawn from active chambers 52 and 52' so that the system can
"catch up." As a result, rather than the piston rods 41 and 41'
smoothly moving in the direction opposite to the floating structure
a distance equal to the movement of the floating structure as shown
by the dashed line 74, the piston rods will oscillate as
illustrated by the dotted line 84.
It has been discovered that such error in the motion compensation
and/or weight control system operated in the position mode can be
substantially reduced if the control means 65 functions responsive
primarily to the data provided by the velocity transducer 78 and
the velocity transducer 81. Accordingly it is preferred that the
control means 65 cause pump 61 to supply and withdraw hydraulic
fluid to and from the active chambers in accordance with the
following equation:
(1) Q = k.sub.1 (Vs) + k.sub.2 (Ve) + k.sub.3 (Le)
wherein Q is the volume of the hydraulic fluid supplied to or
withdrawn from the active chambers, k.sub.1 is a constant, Vs is
the direction and velocity of the movement of the floating
structure, k.sub.2 is a constant, Ve is the difference between the
direction and velocity of the movement of the floating structure
and the direction and velocity of the movement of the piston rods
41 and 41' (herein sometimes referred to as "velocity error"),
k.sub.3 is a constant, and Le is the difference in the position of
the floating structure relative to the wellhead and the position of
the piston rods relative to the outer cylinders (herein sometimes
referred to as "position error"). Although it has been determined
empirically that effective motion compensation and/or weight
control can be obtained when the control means operates responsive
only to velocity data, it is still desirable to utilize position
data to account for drift in the system such as may be caused by
loss of hydraulic fluid and the like.
2. Detailed description of electrical components of active portion
of system
FIG. 4 illustrates partially in schematic and partially in block
diagram a preferred arrangement of the electrical components
comprising the control means 65. The portion of such electrical
components utilized when the system is operated in the position
mode is as follows. Position transducer 80 generates an electrical
signal proportional to the linear position of the floating
structure relative to the wellhead. This electrical signal is added
to an electrical signal generated by potentiometer 85, which is
adjusted to a magnitude proportional to the tide. This combined
electrical signal is coupled to the input of an operational
amplifier 86, such as a type 741. Also coupled to the input of
amplifier 86 is an electrical signal generated by position
transducer 75 which is proportional to the linear position of the
piston rods 41 and 41' relative to the outer cylinders 43 and 43'.
Amplifier 86 functions to compare the two electrical signals
supplied to its input and generate an electrical signal
proportional to the difference therebetween. This electrical signal
generated by amplifier 86 is proportional to the position
error.
Velocity transducer 78 generates an electrical signal proportional
to the direction and velocity of the movement of the piston rods
relative to the outer cylinders. Velocity transducer 81 generates
an electrical signal proportional to the direction and velocity of
the movement of the floating structure relative to the wellhead.
These two electrical signals are coupled to an operational
amplifier 87 which functions to compare them and generate an
electrical signal proportional thereto. The electrical signal
generated by amplifier 87 is proportional to the velocity
error.
The position error signal generated by amplifier 86 and the
velocity error signal generated by amplifier 87 are coupled to an
operational amplifier 88 which functions to compare them and
generate an electrical signal proportional to their sum. The
electrical signal generated by amplifier 88 and the velocity signal
generated by transducer 81 are coupled to operational amplifier 89
which functions to compare the two signals and generate an
electrical signal proportional to their sum. The electrical signal
generated by amplifier 89 is proportional to the volume of
hydraulic fluid which should be supplied to or withdrawn from the
active chambers 52 and 52' to obtain substantially error-free
motion compensation when the system is operated in the position
mode.
The electrical signal generated by amplifier 89 is coupled through
switch 90 to the input of a conversion means 91. Also coupled to
the input of conversion means 91 is an electrical signal generated
by tachometer 92 which is proportional to the speed of the motor
(not shown) driving pump 61. The conversion means 91, any of
numerous devices well known to those skilled in the art, functions
to convert the input electrical signal which is proportional to the
volume of hydraulic fluid to be supplied to or withdrawn from the
active chambers, into an electrical signal which is inversely
proportional to the speed of the pump 61. The output of conversion
means 91 is coupled to the input of non-linear compensation means
93 which functions to alter the electrical signal to compensate for
any non-linearity in the system. The output of non-linear
compensation means 93 is coupled to the input of an operational
amplifier 94. Also coupled to the input of amplifier 94 is a
feedback electrical signal generated by linear variable
differential transformer (LVDT) 95 which functions to transduce the
position of the yoke of pump 61 into an electrical signal
proportional thereto. The amplifier 94 functions to compare the two
electrical signals supplied to its input and generate an electrical
signal proportional to the difference therebetween. The electrical
signal generated by amplifier 94 is coupled to servo driver 96
which functions to supply the desired electrical signals to servo
valve 64. Servo valve 64 is mechanically connected to the yoke of
pump 61.
Once the specifications of a system are determined, the desired
magnitudes of the constants k.sub.1, k.sub.2, and k.sub.3 in
formula (1), as well as the various resistances, capacitances,
inductances to be added to the circuitry and adjustments to the
amplifiers to incorporate the constants k.sub.1, k.sub.2, and
k.sub.3, are easily designable by those skilled in the art with
only a routine amount of experimentation.
In the pressure mode, the control means 65 functions responsive to
the electrical signals generated by the pressure transducer 57 and
the pressure transducer 60 to cause servo valve 64 to operate pump
61 such that hydraulic fluid is supplied to and from the active
chambers 52 and 52'. It has been discovered empirically that when
the system is operated in the pressure mode, there is no need to
monitor the velocity of the movement of the floating structure
relative to the wellhead or the velocity of the movement of the
piston rods relative to the outer cylinders. Proper weight control
may be obtained simply by monitoring the pressure of the hydraulic
fluid in the passive chambers and the pressure of the hydraulic
fluid in the active chambers. Accordingly, it is preferred that the
control means 65 cause pump 61 to supply and withdraw hydraulic
fluid to and from the active chambers in accordance with the
following equation:
(2) Q = (P.sub.1 A.sub.1- P.sub.2 A.sub.2) - K
wherein Q is the volume of the hydraulic fluid supplied to or
withdrawn from the active chambers, P.sub.1 is the pressure of the
hydraulic fluid in the passive chambers, A.sub.1 is the effective
cross-sectional area of the passive chambers, P.sub.2 is the
pressure of the hydraulic fluid in the active chambers, A.sub.2 is
the effective cross-sectional area of the active chambers, and K is
the desired hook load.
It is believed that the reason velocity data is not needed when the
system is operated in the pressure mode, but is desirable when the
system is operated in the position mode, is that the system has a
much faster response to change when operated in the pressure mode.
In the pressure mode, the primary parameter--pressure--is being
monitored and acted upon. In the position mode, a secondary
parameter--position--is being monitored and acted upon (position is
a secondary parameter because it changes after there has been a
change in the pressure of the hydraulic fluid.)
Referring again to FIG. 4, the portion of the preferred electrical
components of the control means 65 utilized in the operation of the
system in the pressure mode will be described. Pressure transducer
57 transduces the pressure of the hydraulic fluid in the passive
chambers 51 into an electrical signal proportional thereto.
Pressure transducer 60 transduces the pressure of the hydraulic
fluid in the active chambers 52 into an electrical signal
proportional thereto. These two electrical signals are coupled to
the input of an operational amplifier 100, such as a 741, which
functions to compare them and generate an electrical signal
responsive to the difference therebetween. The output of amplifier
100 is coupled to the input of operational amplifier 101. Also
coupled to the input of amplifier 101 is an electrical signal
generated by potentiometer 102 which is proportional to the desired
hook load. Amplifier 101 functions to compare the two electrical
signals supplied to its input and generate an electrical signal
proportional to the difference therebetween. The electrical signal
generated by amplifier 101 is coupled through switch 103 to the
input of the conversion means 91. The conversion means 91 and the
remaining components acting responsive to the output of conversion
means 91 are as heretofore explained.
Once the specifications of the system are determined, the various
resistances, capacitances and inductances to be added to the
circuitry and the adjustments to the operational amplifiers to take
into account the areas A.sub.1 and A.sub.2 in formula (2) are
easily designable by those skilled in the art with only a routine
amount of experimentation.
The other preferred electrical components of the control means 65
illustrated in FIG. 4 will now be described. Preferably, the
electrical signal generated by position transducer 75 is coupled to
the input of operational amplifier. Also coupled to the input of
amplifier 104 is an electrical signal generated by potentiometer
106 which is proportional to a selected, desired linear position of
the piston rods 41 relative to the outer cylinders 43. Preferably,
potentiometer 106 is adjusted to generate an electrical signal
proportional to the position of the piston rods 41 either at the
center of their stroke or at the top of their stroke. Amplifier 104
functions to compare the two electrical signals supplied to its
input and generate an electrical signal proportional to the
difference therebetween. The electrical signal generated by
amplifier 104 is coupled through switch 107 to the conversion means
91. When this portion of the circuitry is utilized, switch 107 is
closed and switches 90 and 103 are opened. Amplifier 104 then
generates the necessary electrical signal to cause pump 61 to
supply or withdraw hydraulic fluid to and from the active chambers
such that, irrespective of the movement of the floating structure
or any losses in the system, the piston rods remain at the
selected, desired position, such as, at the center of their stroke
or at the top of their stroke.
Coupled to the output of amplifier 86 is an operational amplifier
109. Coupled to the other input of such amplifier 109 is an
electrical signal generated by potentiometer 110, which is adjusted
to a selected magnitude. Amplifier 109 functions to compare the two
electrical signals supplied to its input and generate a logic
signal responsive thereto. Preferably, the potentiometer 110 is
adjusted whereby the logic signal generated by amplifier 109
indicates whether the position of the piston rods relative to the
center of their stroke equals the position of the floating
structure relative to the center of its range of heave. If this
portion of the circuitry is activated, when the position of the
floating structure relative to the center of its range of heave
equals the position of the piston rods relative to the center of
their stroke, amplifier 109 generates a logic signal which causes
switch 90 to close and switches 103 and 107 to open. The system
then operates in the position mode.
Coupled to the output of amplifier 101 is an operational amplifier
111. Also coupled to the input of amplifier 111 is an electrical
signal generated by potentiometer 112, which is adjusted to a
preselected magnitude. Amplifier 111 functions to compare the two
electrical signals supplied to its input and generate a logic
signal responsive thereto. Preferably, potentiometer 112 is
adjusted whereby the logic signal generated by amplifier 111
indicates when the actual load supported by hook 21 equals the
preselected hook load K in formula (2). If this portion of the
circuitry is activated, when the actual load supported by the hook
equals the preselected hook load, amplifier 111 generates a logic
signal which causes switch 103 to close and switches 90 and 107 to
open. The system then operates in the pressure mode.
3. Operation of system in position mode
The improved motion compensation and/or weight control system
according to this invention preferably is operated in the position
mode when it is desired to maintain a load in a selected position
relative to the earth or to move a load at a selected velocity
relative to the earth. By way of example assume that the
earth-boring assembly illustrated in FIG. 1 is being utilized to
land a 250,000 pound blowout preventer (not shown) on the wellhead
17. Assume that when the last section of drill pipe is added to the
string to lower the BOP to the wellhead, the total load supported
by hook 21 is 300,000 pounds. Assume that the floating structure 13
is experiencing wave heaves six feet in either direction, that is,
moving through a total distance of twelve feet. Assume the movement
range of the piston rods 41 and 41' inside the outer cylinders 43
and 43' is 24 feet. The air in the bank 36 of air accumulator tanks
is pressurized to the magnitude necessary to move piston rods 41
and 41' to the top of or adjacent the top of their movement range.
If the combined effective cross-sectional areas of the passive
chambers is approximately two hundred square inches, the pressure
of the air in the bank 36 of air accumulator tanks will be in the
range of 1500 to 2000 pounds per square inch. The total upward
force supplied by the passive portion of the system will be in the
range of approximately 330,000 pounds.
The portion of the electrical circuitry in FIG. 4 relating to
amplifier 104 is energized by closing switch 107 and opening
switches 90 and 103. Pump 61 is thus caused to actively pump
hydraulic fluid into active chambers 52 and 52' to provide a
downward force opposing the force of the hydraulic fluid in the
passive chambers. If the total effective cross-sectional area of
the two active chambers is approximately 23 square inches, the
pressure of the active fluid supplied to the active chambers will
vary within the range of approximately 150 pounds per square inch
to 2500 pounds per square inch. The pressure of the hydraulic fluid
in the active chambers 52 and 52' is increased until the piston
rods 41 and 41' have been moved downwardly to the position selected
in the adjustment of potentiometer 106, preferably the mid-point of
their movement range. Once the piston rods reach the midpoint of
their movement range. Once the piston rods reach the midpoint of
their movement range, amplifier 104 generates the necessary
electrical signal to keep the piston rods at the midpoint of their
movement range. As a result, the blowout preventer is thus heaving
with the heaving floating structure 13.
The ratio of the effective cross-sectional area of the active
chambers to the passive chambers preferably is 1:4 or less to
reduce the amount of the hydraulic fluid to be moved into and out
of the active chambers, thereby reducing the flow rate of the
hydraulic fluid through the pump 61 and consequently the required
horsepower of the pump 61. Assuming that the maximum heave in which
the motion compensation and/or weight control system will operate
is one that moves the floating structure 20 feet vertically in 18
seconds, the velocity of such heave can approach 5 feet per second.
It has been determined that to compensate for such five foot per
second movement, it may be necessary to move as much as 3100
gallons per minute of hydraulic fluid into and out of the passive
chambers 51 and 51'. But if the cross-sectional area of the active
chambers is one-fourth or less than that of the passive chamber,
then only 730 gallons per minute maximum would have to be actively
pumped into and out of the active chambers 52 and 52'.
When it is desired that the improved motion compensation and/or
weight control system according to this invention operate in the
position mode to maintain the load in a selected position relative
to the earth, the portion of the electrical circuitry in FIG. 4
relating to amplifier 109 is energized. When the floating structure
moves through the center of its range of heave (the piston rods are
being held at the center of their stroke), amplifier 109 emits a
logic signal which closes switch 90 and opens switch 107. Hydraulic
fluid is then actively supplied to and withdrawn from the active
chambers in accordance with formula (1) above. Thus, as the
floating structure 13 moves upwardly, pump 61 will actively supply
hydraulic fluid into active chambers 52 and 52' at the rate
necessary to drive piston rods 41 and 41' downwardly to match the
upward movement of the floating vessel. Downward movement of piston
rods 41 and 41' of course moves first pistons 47 and 47'
downwardly, thereby forcing hydraulic fluid out of the passive
chambers 51 and 51' and back into oil/air interface tank 35. This
compresses the air in the bank 36 of air accumulator tanks and the
oil/air interface tank 35 and causes its pressure to increase. This
increase in the pressure of the air in the bank 36 of air
accumulator tanks is transmitted to the hydraulic fluid in the
passive chambers 51 and 51' and increases the upward forces on
first pistons 47 and 47'. However, since control means 65 is
operating responsive to signals representative of the movement and
the velocity of the movement of the floating structure with respect
to the wellhead and the movement and the velocity of the movement
of piston rods 41 and 41' with respect to outer cylinders 43 and
43', the control means detects the change in the velocity of the
piston rods relative to the outer cylinders as a result of the
change in the pressure of the hydraulic fluid in the passive
chambers and causes pump 61 to supply even more hydraulic fluid to
the active chambers 52 and 52' to overcome these increased upward
forces. When the floating vessel 13 reaches the apex of its upward
movement, the piston rods 41 and 41' have been driven downwardly 6
feet. The pressure of the fluid in the passive chambers will have
increased such that the total upward forces of the passive portion
of the system may be in the range of approximately 360,000
pounds.
When the floating vessel 13 starts back downward, control means 65
causes pump 61 to commence pumping hydraulic fluid out of the
active chambers 52 and 52' and back into the sump 63. Since the
upward forces on the first pistons 47 and 47' are now increased to
approximately 360,000 pounds due to the decrease in the volume of
the air in the passive system, piston rods 47 and 47' and the
300,000 pound load depending therefrom easily and smoothly move
upwardly relative to the outer cylinders 43 and 43' as the floating
structure 13 moves downwardly and hydraulic fluid is pumped out of
the active chambers. Pump 61 continues to withdraw hydraulic fluid
from the active chambers as the piston rods 41 and 41' moves
upwardly, and increases the withdrawal of such hydraulic fluid as
necessary to overcome the pressure losses existing in the physical
components of the system and the pressure losses attendant to the
expansion of the air in the bank 36 of air accumulator tanks and
the oil/air interface tank 35. Thus, as the floating vessel 13
moves upwardly and downwardly 12 feet, the blowout preventer
remains stationary relative to the wellhead.
When the improved motion compensation and/or weight control system
according to this invention operates in the position mode, it is
quite easy to move the load upward or downward at a selected
velocity relative to the earth. For example, assume it is desirable
to lower the blowout preventer into the wellhead from its present
stationary position about the wellhead. This is generally
accomplished by causing the draw works 29 to commence unwinding
cable so that the traveling block 27, the expansible and
contractible mechanism 22, and the load are all lowered toward the
wellhead. The control means 65 will not be cognizant of this change
in the vertical reference position of the BOP and will continue to
generate the necessary electrical signals such that the mechanism
22 will expand and contract to offset the heaves of the floating
structure. The BOP can thus be lowered smoothly into place on the
wellhead.
Although the improved motion compensation and/or weight control
system according to this invention preferably is operated in the
pressure mode to maintain a selected weight on a tool in contact
with the earth (as will hereinafter be explained), the system may
be operated in the position mode to accomplish such task. Assume
that the hook 1 is supporting a load of 300,000 pounds comprising
15,000 feet of drill string with a drill bit on its lower end.
Assume the toolpusher wishes to maintain a pressure of 50,000
pounds between the drill bit and the earth. The motion compensation
and/or weight control system must therefore supply an upward force
of 250,000 pounds to the load. This 250,000 pound load on the hook
21 is the hook load.
The air in the bank 36 of air accumulator tanks is pressurized to a
magnitude sufficient to raise piston rods 41 and 41' to the top of
their stroke or a point adjacent the top of their stroke. Pump 61
is then caused to supply hydraulic fluid into active chambers 52
and 52' sufficient to move piston rods 41 and 41' back downward to
the mid-point of their strokes. Thereafter, control means 65
operates responsive to the electrical signals from transducers 81
and 78 and 80 and 75 to cause pump 61 to supply or withdraw
hydraulic fluid to or from the active chambers 52 and 52'
responsive to the movement of the floating structure 13 relative to
the wellhead and the movement of the piston rods 41 and 41'
relative to the outer cylinders 43 and 43'. The toolpusher
operating the earth-boring apparatus maintains the desired 250,000
pound hook load by viewing a dead weight indicator 30 in the cable
26 and operating the drawworks 29 responsive thereto or by causing
the drawwords 29 to operate automatically responsive to the dead
weight indicator 30. Any vertical movement of the floating
structure 13 is compensated for by the the improved motion
compensation and/or weight control system according to this
invention as heretofore described.
4. Operation of system in pressure mode
Although the improved motion compensation and/or weight control
system according to this invention preferably is operated in the
position mode to maintain a tool in a selected vertical position
(as explained above), the system may also be operated in the
pressure mode to maintain a tool in a selected vertical position.
For example, assume that the system is supporting a 300,000 pound
load comprising a 250,000 pound blowout preventer (not shown) and
the drill string to which the BOP is secured. Assume that this
blowout preventer is being held ten feet above the wellhead. The
air in the bank 36 of accumulator tanks is pressurized to the
extent necessary to raise piston rods 41 and 41' the top of their
strokes or a point adjacent the top of their strokes. Since the
load is 300,000 pounds, the upward forces supplied by the hydraulic
fluid in the passive chambers will be somewhat in excess of 300,000
pounds. Potentiometers 102 and 112 are adjusted to generate
electrical signals proportional to the 300,000 pound hook load
being supported. Pump 61 is caused to supply fluid into the active
chamber 52 and 52' to the extent necessary to force the piston rods
41 and 41' downward, thereby increasing the pressure of the
hydraulic fluid in the passive chambers and the resultant upward
forces of such fluid. When the difference between the downward
forces of the fluid in the active chambers and the upward forces of
the fluid in the passive chambers equals the preselected hook load
of 300,000 pounds as stated in formula (2), amplifier 111 generates
the necessary logic signal to close switch 103 and open switches 90
and 107.
If floating vessel 13 commences to move upwardly, the blowout
preventer will resist such upward motion due to gravity, its own
inertia, and the water drag against its water plane area. This will
cause the piston rods 41 and 41' to move downwardly and the
pressure of the hydraulic fluid in the passive chambers 51 and 51'
will increase. Control means 65 will, responsive to signals from
pressure transducers 57 and 60, cause pump 61 to supply additional
hydraulic fluid to the active chambers to increase the downward
force generated by the hydraulic fluid in such active chambers. The
system is operated such that the upward force of the hydraulic
fluid in the passive chambers, minus the downward force of the
hydraulic fluid in the active chambers, continues to equal the
selected upward force of 300,000 pounds necessary to maintain the
BOP stationary.
As the floating vessel 13 moves downwardly in the water, the outer
cylinders 43 and 43' will move downwardly. The forces of gravity
pulling downward on the blowout preventer will be opposed by the
inertia of the blowout preventer, the water drag against the
blowout preventer, and the upward forces of the fluid in the
passive chambers against pistons 47 and 47'. The upward force of
the fluid in the passive chambers will be considerably in excess of
the hook load and will move piston rods 41 and 41' upwardly
smoothly and affirmatively. As the piston rods move upwardly, the
pressure of the hydraulic fluid in the passive chambers 52 and 52'
will decrease. Control means 65 will then cause pump 61 to withdraw
additional hydraulic fluid from the active chambers 51 and 51' to
decrease the downward forces of the hydraulic fluid in the active
chambers whereby the algebraic sum of the upward forces generated
by the passive fluid and the downward forces generated by the
active fluid continues to equal the 300,000 pound hook load.
The motion compensation and/or weight control system preferably is
operated in the pressure mode when it is desired to maintain a
selected weight on a tool in contact with the earth. Assume the
system is being used with an earth-boring assembly mounted on a
floating structure. Assume the hook 21 is supporting a total load
of 350,000 comprising a drill string and drill bit. Assume that the
toolpusher wishes to maintain the drill bit in contact with the
earth at a pressure of 50,000 pounds. The hook load will then be
300,000 pounds.
The air in the bank 36 of air accumulator tanks is pressurized to
the magnitude necessary to move piston rods 41 and 41' to the top
or near the top of their movement range with the entire 350,000
pound load supported by the hook. As previously explained,
sufficient hydraulic fluid is supplied by pump 61 into the active
chambers to lower the piston rods downward to the mid-point of
their movement range. The control means 65 is then set whereby the
system operates in the position mode and pump 61 introduces and
withdraws hydraulic fluid into and out of the active chambers to
maintain the drill string stationary relative to the earth. Cable
26 is then unwound from draw works 29 to the extent necessary to
lower traveling block 27 and the expansible and contractible
mechanism 22 sufficiently to place the drill bit in contact with
the earth. The toolpusher will be aware that the earth has been
contacted by the dead weight indicator 30 secured in cable 26 as
illustrated in FIG. 1.
Potentiometers 102 and 112 are then adjusted to generate electrical
signals proportional to the desired hook load, that is, 300,000
pounds, and the circuitry attendant to amplifier 111 is energized.
The toolpusher continues to unwind cable from the draw works. When
the earth is supporting 50,000 pounds of the load and the
expansible and contractible mechanism is supporting 300,000 pounds,
the load being supported by mechanism 22 equals the selected hook
load. At that point in time, amplifier 111 generates a logic signal
which closes switch 103 and opens switch 90. As the drill bit
continues to move into the earth and the floating structure heaves,
control means 65 operates in accordance with formula (2) above the
cause pump 61 to introduce and withdraw hydraulic fluid to and from
the active chambers so that the expansible and contractible
mechanism 22 will maintain a constant 300,000 pound upward force on
the load. Thus the system operates as an "automatic driller."
If the motion compensation and/or weight control system according
to this invention is being used as an automatic driller in
connection with a stationary earth-boring apparatus (such as a land
rig), there is no need to move the piston rods 41 and 41' downward
a selected distance from the top of their movement range prior to
commencing drilling. This downward movement of the piston rods is
simply to give the expansible and contractible mechanism 22 room to
contract in order to compensate for the possible downward movement
of the floating structure. The rest of the procedure for operating
the system would be as previously explained.
In addition, if drawworks 29 is equipped with a commercially
available automatic driller, such as the automatic driller
manufactured by Martin-Decker, which can unwind the cable 26
responsive to a selected signal, the improved motion compensation
and/or weight control system according to this invention can
accomplish another desirable function. When the system is being
operated in the pressure mode as an "automatic driller," position
transducers or limit switches (not shown) attached to the
expansible and contractible mechanism can be utilized to determine
when piston rods 41 and 41' have moved downwardly a selected
distance. Upon this occurrence, a selected signal can be
transmitted to drawworks 29 to cause it to unwind a selected amount
of cable 26. Unwinding the cable causes the traveling block 27 to
be moved downwardly a selected distance. This downward movement of
the traveling block ordinarily would increase the hook load.
However, as the traveling block moves downwardly and the hook load
tends to increase, control means 65 will sense the increase in the
pressure of the hydraulic fluid in the passive chambers and
transmit the necessary signal to pump 61 to cause it to withdraw
fluid from the active chambers. Piston rods 41 and 41' will then
move upwardly to maintain the selected 300,000 pound hook load.
5. Certain additional advantages
By increasing the pressure of the air in the passive portion of the
system to a magnitude sufficient to move the piston rods to the top
of their movement range and then utilizing the active portion of
the system to bias the piston rods back down to the midpoint of
their movement range, the improved motion compensation and/or
weight control system of this invention is capable of obtaining
maximum accuracy in supporting its load at all points within the
telescoping movement range of its expansible and contractible
mechanism, but with a minimum of horse-power.
The motion compensation and/or weight control system according to
this invention can, due to the interaction of the passive and
active portions of the system, provide rapid, smooth, and positive
telescoping of its expansible and contractible mechanism, even with
heavy hook loads. This is because, on the one hand, the passive
portion of the system, unlike purely passive systems, is
pressurized to a magnitude sufficient to move the load upward to
the furthest limit of the movement range of the expansible and
contractible mechanism. This is also because, on the other hand,
only relatively small volumes of hydraulic fluid, compared with
purely active systems, need be supplied to or withdrawn from the
system to bias the expansible and contractible mechanism to any
point of its movement range.
The improved motion compensation and/or weight control system
according to this invention has still other advantages over prior
purely passive or active systems. For example, even with a given
magnitude load, it is often necessary to lift the load a selected
distance, such as lifting the drill string to set it on the slips.
When a purely passive motion compensation and/or weight control
system is utilized to so lift the drill string, the pressure of the
air in the bank of accumulator tanks must be increased to raise the
piston rod above its normal operating position. As these is a large
volume of air in the bank of accumulator tanks, considerable
horsepower may be utilized. Once the drill bit is to again contact
the earth, air must be bled out of the bank of accumulator tanks.
In the motion compensation and/or weight control system according
to this invention, the air in the bank of accumulator tanks is
pressurized only once for any given load--to a magnitude sufficient
to move the piston rods to the top of their stroke. Thereafter,
downward movement of the piston rod is accomplished by providing
hydraulic fluid to the active chambers. There is much less
horse-power utilized in moving a relatively small volume of a
non-compressible hydraulic fluid into and out of the active
chambers than in repeatedly pressurizing and de-pressurizing a
relatively large volume of a compressible gas.
The embodiment of the expansible and contractible mechanism 22
illustrated in FIGS. 1 and 2 is additionally advantageous in that
the active chambers function as deceleration means. If the load
should suddenly part and piston rods 41 and 41' move upwardly
rapidly, the upward movement of pistons 47 and 47' will tend to
force the hydraulic fluid in the active chambers back through
conduit 59 and pump 61 into sump 63. The orifices 58 and 58' will
restrict this flow and cause the hydraulic fluid in the active
chambers to resist the upward movement of the piston rods. Of
course the pressure of the hydraulic fluid in the active chambers
will increase dramatically. If the inner cylinder 46 was not
contained within the piston rod 41, the size of the inner cylinder
would have to be substantially larger to withstand these great
pressures. But in the embodiment of the invention disclosed in
FIGS. 1 and 2, as the piston rods 41 and 41' move rapidly upward
and cause the pressure of the active hydraulic fluid to increase,
the piston rods themselves provide the necessary external support
for the inner cylinders 46 and 46' to withstand this increased
pressure.
In the embodiment of the motion compensation and/or weight control
system illustrated in FIGS. 1 and 2, the load is attached to hook
21 at an elevation below that at which support member 42 attaches
to piston rods 41 and 41'. This produces a stability not found in
certain prior art systems in which the piston rods straddle and
extend below the hook and the load is attached to the hook at an
elevation above that at which the support member attaches to the
piston rod.
In the embodiment of the motion compensation and/or weight control
system illustrated in FIGS. 1 and 2, the system, when operated in
the position mode, provides compensation for a certain degree of
lateral movement of the floating structure. If the floating
structure should move laterally from above the wellhead, additional
cable 79 will be unwound from drum 38. Control means 65, operating
responsive to signals received from the position and velocity
transducers 80 and 81 associated with drum 38, will then cause pump
61 to supply additional hydraulic fluid to the active chambers to
compensate for this lateral movement.
B. alternative means for actively supplying and withdrawing
hydraulic fluid to and from active portion of system
FIG. 5 illustrates an alternate means 37 for actively supplying and
withdrawing hydraulic fluid into and from the active chambers 52
and 52'. An auxiliary compensating cylinder 116 is secured by
vertical members 117 to the floating structure 13. Movable
longitudinally within compensating cylinder 116 is a compensating
piston 118. Piston 118 is slidably sealed against the interior of
cylinder 116 by seal ring 119. Depending from the compensating
piston 118 is a piston rod 120. Piston rod 120 extends through the
lower end of compensating cylinder 116 and is slidably sealed
thereagainst by seal ring 121. Secured to the lower end of piston
rod 120 is a cable 122 which is secured to the sea bottom directly
or otherwise.
The variable chamber 123 formed beneath piston 120 and within
compensating cylinder 116 is the auxiliary compensating chamber
123. A port 124 is provided in the lower portion of compensating
cylinder 116. Conduit 59 from the active chambers 52 and 52' (FIG.
2) provides fluid communication between the compensating chamber
123 and the active chambers 52 and 52'.
In operation, hydraulic fluid at a selected pressure is introduced
into the closed system comprising the active chambers 52 and 52',
conduit 59, and compensating chamber 123, by means (not shown) well
known to those skilled in the art. The pressure of such active
hydraulic fluid and the effective cross-sectional area of
compensating chamber 123 are chosen such that the downward force of
the hydraulic fluid in active chambers 52 and 52' against active
pistons 50 and 50' will substantially compensate for the errors in
the passive portion of the system. As the floating structure 13
moves vertically, compensating piston 118 will move vertically. The
increasing and decreasing volume of compensating chamber 123 allows
the active hydraulic fluid to flow through conduit 59 between the
active chambers 52 and 52' and the compensating chamber 123.
For example, assume that the motion compensation and/or weight
control system is supporting a 300,000 pound hook load. Assume that
the air in bank 36 of air accumulator tanks (FIG. 2) has been
pressurized to approximately 330,000 pounds. Assume that the
cross-sectional area of compensating chamber 123 and the pressure
of the hydraulic fluid therein is such that, with compensating
piston 118 in the mid-point of its movement range, the downward
force produced by the hydraulic fluid in active chambers 52 and 52'
against active pistons 50 and 50' is approximately 30,000 pounds.
Assume that the piston rod 41 and 41' are stabilized in the
mid-point of their movement range and the 300,000 pound hook load
is being supported at equilibrium.
If floating structure 13 now moves upwardly, piston rods 47 and 47'
will move downwardly with the load. Hydraulic fluid will be forced
out of the passive chambers 51 and 51' into the oil/air interface
tank 35, thereby compressing the air in the oil/air interface tank
and the bank 36 of air accumulator tanks. As the air is compressed,
its pressure will increase. Thus, piston rods 41 and 41' will not
move downward as far as they should to compensate for the upward
movement of the floating structure 13. However, as floating
structure 13 moves upward, compensating piston 118 is pulled
downward in compensating cylinder 116. This decreases the volume of
compensating chamber 23 and forces hydraulic fluid from
compensating chamber 123 through conduit 59 into the active
chambers 52 and 52'. The pressure ofthe hydraulic fluid contained
in compensating chamber 123 and the cross-sectional area of
compensating chamber 123 has been chosen such that the increased
force against active pistons 50 and 50' in active chambers 52 and
52' substantially equals and cancels the increase in the pressuure
of the hydraulic fluid in the passive chambers 51 and 51'. Thus,
the piston rods 41 and 41' are moved downwardly to their proper
position to compensate for the upward movement of floating
structure 13.
When floating structure 13 moves downwardly, the undesirable drop
in the pressure of the hydraulic fluid in the passive chambers 51
and 51' due to the expansion of the air in the oil/air interface
tank and the bank of air accumulator tanks is compensated for by
compensating piston 118 moving upwardly and allowing hydraulic
fluid to flow from the active chambers 52 and 52' back to
compensating chamber 123.
C. alternative expansible and contractible mechanism
FIG. 6 illustrates an alternate embodiment of the expansible and
contractible mechanism 22 of the improved motion compensation
and/or weight control system according to this invention wherein
the expansible and contractible mechanism 22 is designed to be
releasably secured between the traveling block and the load. This
embodiment of the expansible and contractible mechanism is
constructed identical to the expansible and contractible mechanism
described in FIG. 2, but preferably comprises a single piston and
cylinder assembly, rather than two identical piston and cylinder
assemblies. Preferably, outer cylinder 43 has an eyelet 127 secured
thereto for engagement with a hook 128 depending from the traveling
block 27. The single piston and cylinder assembly is constructed
identical to the piston and cylinder assembly 39 described in FIG.
2. Preferably hook 21 is secured to piston 50 at the lower end of
piston rod 41. Hook 21 engages with an eyelet 129 secured to the
top of swivel 20.
The operation of the motion compensation and/or weight control
system with such expansible and contractible mechanism 22 is as
previously explained with respect to the system illustrated in
FIGS. 1 through 5. Either the control means 65 and related
equipment illustrated in FIG. 2 or the means 37 illustrated in FIG.
5 may be utilized to move hydraulic fluid into and out of the
active chamber 52.
When an earth-boring assembly is being utilized to "trip" drill
string into and out of the hole, expansible and contractible
mechanism 22 illustrated in FIG. 6 may be disconnected from the
traveling block 27 and stored inside the derrick or on the floating
structure 13. This eliminates weight during the "tripping" cycle
and thus reduces cable wear and pulley wear. When the earth-boring
apparatus again requires the use of the motion compensation and/or
weight control system, the expansible and contractible mechanism 22
can be reattached beneath the traveling block 27.
D. motion compensation and/or weight control system utilized with
an earth-boring assembly having a drillhead
FIG. 7 illustrates an alternate embodiment of the improved motion
compensation and/or weight control system according to this
invention wherein the system is adapted for use with an
earth-boring assembly utilizing a drill head rather than cables and
blocks. Secured to floating structure 13 are vertical members 131
which support a horizontal support member 132. Secured to
horizontal support member 132 is an expansible and contractible
mechanism 22 according to this invention such as is illustrated and
described in FIG. 2. Depending from the two piston rods 41 and 41'
is a drill head assembly 133 such as is well known to those skilled
in the art. Depending from the drill head assembly 133 is a drill
string 14.
The operation of the system is as previously explained with respect
to FIGS. 1 through 5. Hydraulic fluid preferably is supplied to and
withdrawn from the active chambers 52 of the expansible and
contractible mmechanism 22 by the control means 65 and related
equipment illustrated in FIG. 2 or the means 37 illustrated in FIG.
5.
E. alternative expansible and contractible mechanism
FIG. 8 illustrates an alternate embodiment of the expansible and
contractible mechanism 22 of the improved motion compensation
and/or weight control system according to this invention. Secured
between a first support member 134 and a second support member 135
are two passive piston and cylinder assemblies 136 and 136' and two
active piston and cylinder assemblies 137 and 137'. The piston and
cylinder assemblies could of course extend upward on either side of
the traveling block 27. As previously explained, the forces
produced by the active piston and cylinder assemblies 137 and 137'
oppose the forces produced by the passive piston and cylinder
assemblies 136 and 136'. The operation of the motion compensation
and/or weight control system with the expansible and contractible
mechanism 22 illustrated in FIG. 8 is as previously described with
respect to FIGS. 1 through 5. Hydraulic fluid preferably is
supplied to and withdrawn from each of the active piston and
cylinder assemblies either by the control means 65 and related
equipment illustrated in FIG. 2 or the means 37 illustrated in FIG.
5.
F. alternative expansible and contractible mechanism
FIG. 9 illustrates still another embodiment of an expansible and
contractible mechanism 22 of the improved motion compensation
and/or weight control system according to this invention. Secured
to traveling block 27 is a support member 40. Secured to support
member 40 on either side of traveling block 27 is a cylinder 138
and 138'. Movable longitudinally within each cylinder 138 and 138'
is a piston 139. Extending upwardly from each of the pistons 139 is
a relatively large piston rod 140 and 140'. Pivotally attached to
the top of each of the piston rods 140 and 140' is a pulley 141 and
141'. A cable 142 and 142' is reeved around pulleys 141 and 141'
and extended downwardly through an opening (not shown) in support
member 40. Cables 142 and 142' are secured to a support member 143
from which depends hook 21.
The variable chambers 144 beneath the pistons 139 are the passive
chambers. The annular chambers 145 formed between piston rods 140
and 140' and cylinders 138 and 138' are the active chambers. Piston
rods 140 and 140' are preferably formed to have a large
cross-sectional area such that the cross-sectional area of the
annular active chambers 145 are one-fourth or less the
cross-sectional area of the passive chambers 144. Hydraulic fluid
is supplied and withdrawn from the passive chambers through conduit
146. Hydraulic fluid is supplied to and withdrawn from the active
chambers through conduit 147. The means for supplying hydraulic
fluid to the passive chambers preferably is as illustrated in FIG.
2. The means for providing hydraulic fluid to the active chambers
preferably is as illustrated in FIG. 2 or as illustrated in FIG.
5.
The operation of the motion compensation and weight control system
utilizing the expansible and contractible mechanism 22 illustrated
in FIG. 9 is as previously described: the forces of the hydraulic
fluid in the active chambers 145 against pistons 139 oppose the
forces of the hydraulic fluid in the passive chambers 144 against
pistons 139. However, rather than the algebraic sum of the forces
being supplied in a direct mechanical relationship to hook 21, such
forces are doubled by being supplied through the piston rods 140
and 140' carrying pulleys 141 and 141' and cables 142 and 142'.
This allows the stroke of the piston rods 140 and 140' to be
halved.
G. alternative embodiment of motion compensation and/or weight
control system
FIG. 10 illustrates still another embodiment of the improved motion
compensation and/or weight control system according to this
invention. The manner of employing the expansible and contractible
mechanism 22 within a derrick or otherwise is not shown. Extending
longitudinally within and depending from outer cylinder 43 is an
inner cylinder 46. Movable longitudinally within the annular
chamber between the inner cylinder 46 and the outer cylinder 43 is
a first piston 47. Attached to the first piston 47 is a piston rod
41 which slides along the outside of inner cylinder 46. Secured to
the lower end of piston rod 41 is second piston 50. Inner cylinder
46, first piston 47, piston rod 41, and outer cylinder 43 are all
secured in a slidable, sealing relationship whereby a primary
chamber 51 and a secondary chamber 52 are formed similarly as
described with respect to FIG. 2. Hydraulic fluid is passively
supplied to primary chamber 51 through conduit 55 from an oil/air
interface tank 35 and a bank 36 of air accumulator tanks as
described with respect to FIG. 2.
However, unlike the previous embodiments of the improved motion
compensation and weight control system according to this invention,
a second port 150 is provided near the bottom of primary chamber
51. A conduit 151 connects between this second port 150 and a port
152 at the top of secondary chamber 52. Thus, secondary chamber 51
is in fluid communication with primary chamber 52.
The principal of operation of this alternate embodiment of the
invention is as previously described: the force of the hydraulic
fluid in the primary chamber 51 against piston 47 is opposed by the
force of the hydraulic fluid in the secondary chamber 52 against
piston 50. However, in this embodiment the same hydraulic fluid is
supplied to both the primary and secondary chambers.
In operation, assume that piston rod 41 is supporting a 300,000
pound load. The air in accumulator bank 36 is pressurized to a
magnitude sufficient to support such load and move piston rod 41 to
the approximate mid-point of its movement range. The pressure of
the hydraulic fluid will be the same in the primary chamber 51 and
the secondary chamber 52. Assuming that the ratio of the
cross-sectional area of the primary chamber to the secondary
chamber is precisely 4:1, the upward force of the hydraulic fluid
against piston 47 may be 400,000 pounds and the downward force of
the hydraulic fluid against piston 50 may be 100,000 pounds.
Now assume that the floating structure with which the system is
associated moves upwardly. Piston rod 41 will move downwardly with
respect to cylinder 43. As piston rod 41 moves downwardly,
three-fourths of the hydraulic fluid displaced from primary chamber
51 is forced into oil/air interface tank 35 and one-fourth of the
hydraulic fluid displaced from primary chamber 51 is forced into
secondary chamber 52. Movement of three-fourths of the hydraulic
fluid into the oil/air interface tank 35 compresses the volume of
the air therein and in bank 36 of the air accumulator tanks and
causes the pressure of such air to increase. Increasing the
pressure of the air in the air accumultor tanks increases the
pressure of the hydraulic fluid in both the primary chamber 51 and
the secondary chamber 52. Increasing the pressure of the hydraulic
fluid in the primary chamber 51 will, as previously described,
cause an error in the compensation. However, the opposing downward
force of the hydraulic fluid in the secondary chamber 52 is also
increased somewhat due to the increasee of the pressure of the
hydraulic fluid contained therein. This increase in the opposing
force produced by the hydraulic fluid in the secondary chamber 52
decreases the total error in the compensation or weight
control.
Thus, the embodiment of the invention illustrated in FIG. 10 is a
modified passive system wherein the compensation losses inherent in
the prior art purely passive systems are decreased.
From the foregoing, it will be understood that this present
invention provides an improved method and apparatus for motion
compensation and/or weight control. It will now be apparent to
those skilled in the art that the foregoing disclosure and
description of the invention is illustrative and explanatory
thereof, and various changes may be made in the construction of the
improved method and apparatus within the scope of the appended
claims without departing from the spirit of the invention.
* * * * *