U.S. patent number 3,792,715 [Application Number 05/344,593] was granted by the patent office on 1974-02-19 for single seat holding valve.
This patent grant is currently assigned to Koehring Company. Invention is credited to Donald J. Blenderman, John T. Parrett.
United States Patent |
3,792,715 |
Parrett , et al. |
February 19, 1974 |
SINGLE SEAT HOLDING VALVE
Abstract
A holding valve for regulating the exhaust flow of fluid from a
hydraulic actuator including a cartridge defining a first port
adapted to be connected to a directional control valve, a second
port adapted to be connected to one side of the hydraulic actuator
and a third port adapted to be connected to the other side of the
hydraulic actuator, there being provided a pilot operated poppet
valve that closes in opposition to fluid pressure in the actuator
through the second port to control exhaust flow from the actuator
and also to prevent exhaust flow when the directional valve is in
neutral, there also being provided a check valve surrounding the
poppet valve for the purpose of permitting the free flow of line
pressure from the first port to the second port and the hydraulic
actuator, with this check valve being annular in configuration,
surrounding the poppet valve and having a shoulder defining the
seat for the poppet valve to improve the characteristics of the
holding valve and also to permit the simple replacement of the main
poppet valve seat when necessary.
Inventors: |
Parrett; John T. (St. Joseph,
MI), Blenderman; Donald J. (Benton Harbor, MI) |
Assignee: |
Koehring Company (Benton
Harbor, MI)
|
Family
ID: |
23351179 |
Appl.
No.: |
05/344,593 |
Filed: |
March 26, 1973 |
Current U.S.
Class: |
137/493; 137/508;
91/420; 137/596.2 |
Current CPC
Class: |
F15B
13/01 (20130101); F15B 11/04 (20130101); F15B
2211/50545 (20130101); F15B 2211/5153 (20130101); F15B
2211/7053 (20130101); Y10T 137/7834 (20150401); F15B
2211/75 (20130101); F15B 2211/528 (20130101); Y10T
137/87241 (20150401); Y10T 137/7771 (20150401); F15B
2211/30525 (20130101) |
Current International
Class: |
F15B
11/00 (20060101); F15B 13/00 (20060101); F15B
13/01 (20060101); F15B 11/04 (20060101); F16k
011/10 () |
Field of
Search: |
;137/596.2,493,596.1,493.1,493.6,493.8,469,472,473,87,508,596.13,596.14 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Scott; Samuel
Assistant Examiner: Miller; Robert J.
Attorney, Agent or Firm: Hofgren, Wenger, Allen, Stellman
& McCord
Claims
We claim:
1. A holding valve assembly for controlling flow between a flow
control valve and a fluid actuator, comprising; first port means
adapted to be connected to receive and deliver fluid relative to
the flow control valve, second port means adapted to be connected
to receive and deliver fluid relative to one side of the actuator,
third port means adapted to be connected to the other side of the
fluid actuator, a check valve for permitting flow from the first
port means to the second port means and preventing flow from the
second port means to the first port means, and a poppet valve
member actuated by fluid pressure in said third port means for
permitting flow from said second port means to said first port
means, said check valve defining a valve seat for said poppet
valve.
2. A holding valve assembly as defined in claim 1, including a
cartridge sleeve surrounding the valves.
3. A holding valve assembly as defined in claim 1, wherein said
check valve has a cylindrical outer surface, and an internal
shoulder defining the valve seat for the movable poppet valve
member whereby the seat for the poppet valve member is movable.
4. A holding valve assembly as defined in claim 1, including a stop
for limiting movement of said check valve in the direction of
opening movement of the poppet valve member.
5. A holding valve assembly as defined in claim 1, wherein said
poppet valve member has a pilot piston on the end thereof between
said second and third port means.
6. A holding valve assembly as defined in claim 1, including a
heavy spring urging said poppet valve to a closed position against
the force of fluid in the second port means.
7. A holding valve assembly as defined in claim 1, including a stop
for limiting movement of the poppet valve member in a closing
direction.
8. A holding valve assembly for controlling flow between a flow
control valve and a fluid actuator, comprising; a valve bore, first
port means communicating with said valve bore and adapted to be
connected to the flow control valve, second port means
communicating with said bore and adapted to be connected to one
side of the actuator, third port means communicating with said bore
and adapted to be connected with the other side of the actuator, a
sleeve shaped check valve slidable in said bore for preventing flow
from said second port means to said first port means and permitting
flow from said first port means to said second port means, said
sleeve shaped check valve having an inside shoulder defining a
movable valve seat, a stop within said bore for limiting movement
of sleeve shaped check valve, a spring in said bore biasing said
check valve toward said stop, a poppet valve in said bore actuated
by fluid pressure in said third port means for selectively
preventing fluid flow from said second port means to said first
port means or permitting fluid flow from said second port means to
said first port means, said poppet valve being seated on the seat
defined by sleeve shaped check valve, a stop for said poppet valve
holding said poppet valve in a position preventing flow from the
second port means to said first port means, and a second spring
stronger than said first spring for urging the poppet valve toward
said stop against the fluid pressure in said second port means,
said check valve and poppet valve opening in opposite
directions.
9. A holding valve assembly, as defined in claim 8, wherein said
bore is defined by a cartridge sleeve.
10. A holding valve assembly, as defined in claim 8, including a
pilot piston at the end of the poppet valve slidable in an enlarged
counterbore in said valve bore.
Description
BACKGROUND OF THE PRESENT INVENTION
Pilot operated holding valves have been provided in the past for
regulating the exhaust flow from a hydraulic actuator. The primary
purpose of these holding valves is to control the lowering of a
load connected to the hydraulic actuator. With the pilot piston
that operates the poppet valve connected to one side of the
actuator the poppet valve controls exhaust flow from the other side
of the actuator, so that if the load tends to overrun, the pressure
in the load lowering side of the actuator will drop, reducing pilot
pressure which in turn tends to close the main poppet valve and
restrict the exhaust flow from the actuator and reduce the speed of
load lowering to a controlled condition.
It is also known in the art to provide a bypass check valve that
permits the free flow of fluid from a directional control valve to
the load raising side of the actuator for the purpose of bypassing
the poppet holding valve.
There have been several problems associated with these prior art
pilot operated holding valves. The first results from the fact that
the seat for the main poppet valve is formed in prior art
constructions either in the holding valve housing, or cartridge. If
deterioration of the seat occurs, which it oftentimes does, it is
necessary to replace the holding valve housing or remachine the
seat which is a difficult and expensive machining operation.
Other disadvantages in prior art holding valves are that it is
difficult to control the effective area of the poppet upon which
cylinder pressure acts and also difficult to control the area of
the poppet valve upon which pilot pressure acts. These parameters
control the responsiveness of the valve and also control the change
of the size of the poppet valve orifice with changes in travel or
movement of the poppet valve.
SUMMARY OF THE PRESENT INVENTION
In accordance with the present invention an improved holding valve
is provided in which the main valve seat may be easily replaced and
in which the various areas that control the valve characteristics
may be easily changed to control the performance of the valve in a
simpler manner than prior art constructions.
Toward this end a counter-balance holding valve is provided that
has a cartridge sleeve defining a first port communicating with a
directional control valve, a second port connected to one side of
the hydraulic actuator and a third port connected to the other side
of the hydraulic actuator. Disposed within this sleeve is a pilot
operated main poppet valve that controls and regulates flow from
the second port to the first port to control the lowering of the
load connected to the hydraulic actuator. This main poppet valve
also serves to hold the load in position by preventing flow from
the second port to the first port when the directional control
valve is in neutral.
To provide for forward flow from the control valve to the actuator,
and hence from the first port to the second port in the sleeve, a
check valve is provided that is annular in configuration, slidable
in the cartridge sleeve, and surrounding the main poppet valve.
This check valve has the novel characteristic that its internal
bore defines a seat for the main poppet valve. In this manner when
deterioration of the poppet valve seat occurs it is merely
necessary to replace the inexpensive check valve, since it also
defines the seat for the main poppet valve.
The term "percentage characteristic" refers to the sensitivity of
the poppet valve in response to variations in pilot pressure acting
on the poppet valve and is equal to the area of the poppet valve
against which cylinder pressure acts divided by the area of the
poppet valve against which pilot pressure acts. A higher pilot
piston area relative to the cylinder pressure area referred to
means that a lower pilot pressure is required to open the main
poppet valve and hence the valve has an increased sensitivity.
This percentage characteristic can be easily varied in the present
holding valve since the area of the poppet valve against which
cylinder pressure acts may be made either positive, balanced or
even negative if desired, and the pilot piston area may also be
easily varied as desired.
A further advantage in the present invention is that fluid flow
passing through the valve in either direction does not pass through
the coils of either the poppet valve spring or the spring urging
the check valve closed.
Further advantages are that a thermal relief valve may be easily
provided and the main counterbalance spring may be adjusted as
desired.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a plan view of the cartridge holding valve according to
the present invention;
FIG. 2 is an enlarged longitudinal section of the holding valve
shown in FIG. 1 taken generally along line 2--2 thereof illustrated
in conjunction with a typical fluid actuator circuit shown
schematically; and
FIG. 3 is a longitudinal section of a somewhat modified form of the
holding valve illustrated in FIG. 1 and 2.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring to the drawings and particularly FIGS. 1 and 2 a
cartridge type holding valve 10 is illustrated in circuit with a
4-way directional control valve 12 and a reciprocating piston
hydraulic actuator 14 shown schematically in FIG. 2.
The 4-way control valve 12 selectively ports fluid from a supply
line 16 to line 18 to the right side 20 of actuator 14 which drives
piston 21 in what may be assumed to be a load lowering direction,
or to line 23 through holding valve 10 to line 24 connected to the
left side 26 of actuator 14 to drive the piston 21 in what may be
assumed to be a load raising direction.
The primary purpose of the holding valve 10 is to control the speed
of piston 21 when moving in a load lowering direction to control
the smooth lowering of the load connected to the piston 21. Holding
valve 10 also serves to lock the piston 21 in position when the
directional control valve 12 is in its neutral position.
The holding valve 10 includes a stepped cylindrical cartridge
sleeve 30 seated within a stepped counterbore 31 in valve housing
32 and threaded therein as seen at 34. Sleeve 30 has a hexagonal
head portion 35 projecting from the housing 32 and sealed thereto
with a sealing ring 36.
The sleeve 30 has lands 39 and 40 that define recesses for seal
assemblies 42 and 43 in turn defining annular recesses 46, 47 and
48 around the periphery of the sleeve 30 within the housing 32.
The sleeve 30 has a first annular array of ports 50 communicating
across recess 46 with housing port 48 connected to fluid supply and
return line 23.
The sleeve 30 has a second annular array of ports 50' communicating
across recess 37 with housing port 52 connected to receive and
deliver fluid relative to line 24 connected to actuator 14. The
sleeve 30 has a reduced annular end portion 55 that is spaced from
the end of counterbore 31 defining a flow passage 56 which
communicates across recess 48 with a port 58 in the housing 32 that
communicates with a pilot pressure line 60 having a restrictor 61
therein. Line 60 communicates with line 18 that delivers fluid to
the right side 20 of cylinder 14.
The sleeve 30 has threaded therein a hollow sleeve cap 62 having a
hexagonal head portion 63 for the purpose of threading the sleeve
62 within the sleeve 30 as indicated at 65.
The cartridge sleeve 30 has a first counterbore portion 67
communicating with port 50, and a somewhat reduced counterbore 68
communicating with a further reduced counterbore 70 in turn
communicating with port 50'. A still further smaller bore portion
73 in turn communicates with a somewhat larger bore 75 opening to
the right end of the sleeve 30 and communicating with passage 56
defined in the housing bore 31.
Slidable within the stepped bore cartridge sleeve 30 is a poppet
valve assembly 77 having a semi-spherical valving surface 78 at the
left end thereof defining with stub shaft 79 a seat for the right
end of a heavy duty counter balance spring 82 that urges the poppet
valve 77 closed in opposition to fluid pressure in actuator chamber
26 as sensed through ports 52 and 50'.
The spring 82 is adjustable through spring seat 85 and threaded
member 87 threadedly engaged in sleeve cap 63 and held in position
by a locking nut 89.
The purpose of poppet valve 77 is to control flow between port 52
and port 48, or more specifically between ports 50' and 50 in the
sleeve 30 to regulate flow from the actuator chamber 26.
Toward this end the valve 77 has a reduced stem portion 91
connected to a somewhat enlarged head 92 having a seal 93 slidable
in cartridge bore 73, in turn connected to an enlarged pilot piston
95 having a sealing ring 96.
Rightward movement of the valve member 77 is limited by a snap ring
98 seated within counterbore 75 in the cartridge sleeve 30.
When the 4-way directional valve 12 is shifted to a position
porting fluid to line 18 and draining fluid from line 23 to tank,
actuator side 20 is pressurized, tending to drive piston 21 to the
left, and also the pilot passage 56 is pressurized across
restrictor 61 and port 58 in housing 32. Upon sufficient
pressurization of the pilot piston 95 valve member 77 will shift to
the left against the force of spring 82, opening valve surface 78
permitting the exhaust flow of fluid from actuator side 26 through
line 24, port 52, recess 47, port 50', bore 70, across the valve
orifice, through ports 99 in sleeve 62, ports 50 in sleeve 30, and
port 48 to line 23 and across the directional control valve 12 to
tank.
If the load on the piston 21 tends to overrun the flow of fluid to
actuator chamber 20, the pressure in chamber 20 will drop somewhat
as will the pressure acting on the pilot piston 98, which in turn
causes a shifting of the valve 77 to the right tending to close the
valve and restrict the return flow of fluid from actuator chamber
26 and thus return load lowering to the desired speed. The
counterbalance valve 77 has a modulating action to control the
exhausting of fluid from the return side 26 of the actuator to
provide smooth load lowering movement.
Provision is made for permitting the free flow of fluid from the
control valve 12 through line 23, port 48 and port 50 across the
poppet valve seat to the port 50', port 52 to line 24 to the left
side 26 of actuator 14 for the purpose of driving piston 21 to the
right. Toward this end a sleeve check valve 101 is provided having
a counterbore that receives a biasing spring 102 that biases the
check valve 101 into engagement with the valve surface 78 of the
main poppet valve 77. A reduced interior shoulder 105 on the check
valve defines a floating seat for the main poppet valve 77. The
advantage in this is that when the valve seat 105 deteriorates, it
is easily replaced merely by replacing the check valve 101. Upon
sufficient line pressure in line 23, check valve 101 will shift to
the right with poppet valve stopped by ring 98, permitting the
forward flow of fluid to the left side of actuator 14.
During the opening movement of the poppet valve 77 the check valve
101 will move slightly to the left therewith holding the main
poppet valve orifice closed until the check valve hits shoulder 107
on the sleeve 62 stopping the check valve. Thereafter the poppet
valve 77 continues its movement to the left under the influence of
pilot pressure on piston 95 opening the poppet valve when the right
side of the actuator 14 is pressurized.
The poppet valve 77 has an aperture 110 extending centrally
therethrough that permits the left side 112 of the pilot piston to
drain into the cavity defined by bore 67 within the cartridge
sleeve.
Diameter D.sub.s equaling the diameter of the main poppet seat is
made as small as possible so that the area of the orifice does not
change significantly as the poppet valve opens.
It is possible to easily vary the pressure area diameters to vary
the characteristics of the valve. Firstly, the diameter D.sub.s is
easily varied.
Moreover the diameter D1 may also be easily varied which in
conjunction with D.sub.2 determines the effective area of the
poppet valve 77 upon which pressure in actuator chamber 26 acts. By
making diameter D.sub.s slightly greater than diameter D.sub.1 the
net pressure acting on the valve member 77 from cylinder pressure
is in a positive direction or to the left. However, the pressure in
the actuator acting on valve 77 may be equal merely by making the
area D.sub.s equal to the area D.sub.1 And moreover the net
cylinder force acting on the valve member 77 can be negative by
making the area defined by diameter D.sub.1 greater than the area
defined by diameter D.sub.s so that cylinder pressure tends to
close the poppet valve 77.
Further advantage in the present invention is that the pilot area
defined by pilot diameter D.sub.p may be selected as desired.
The "percentage characteristic" is defined as the effective area
upon which cylinder pressure acts on the poppet valve divided by
the area of the poppet valve upon which pilot pressure acts. A
higher "percentage characteristic" means that a higher pilot
pressure will be required to fully open the valve than with a low
percentage characteristic. Thus the capability of varying the areas
D.sub.p, D.sub.1 and D.sub.s will vary the valve opening
characteristics of poppet valve 77 as desired for the particular
load application.
A somewhat modified form of the present invention is illustrated in
FIG. 3 wherein a holding valve 110 is seen to include a housing 112
having a threaded cartridge sleeve 113 defining a stepped bore 114
receiving a poppet valve 116 having a valve surface portion 117 at
its left end and pilot piston 118 at its right end. Ports 120, 121,
and flow passage 122 are adapted to be connected to the directional
control valve, one side of the hydraulic actuator, and the other
side of the hydraulic actuator, respectively, as in the embodiment
shown in FIGS. 1 and 2. In the embodiment of FIG. 3 a movable check
valve 130 defines a movable seat 132 for the main poppet valve 116
as in FIGS. 1 and 2 embodiment.
In the FIG. 3 embodiment, however, pilot piston 118 also defines
one of the diameters for determining the effective area of the
poppet valve 116 upon which cylinder pressure acts through ports
121. Moreover plunger 136 limits the opening movement of the poppet
valve 116, while shoulder 138 within the cartridge limits the
movement of the poppet valve 116 to the right towards its closed
position.
The valve shown in FIG. 3 operates in substantially the same manner
as the valve shown in FIGS. 1 and 2 so that detailed description
thereof is not believed necessary.
* * * * *