U.S. patent number 3,898,917 [Application Number 05/438,311] was granted by the patent office on 1975-08-12 for variable displacement fluid translating device.
This patent grant is currently assigned to Abex Corporation. Invention is credited to Cecil E. Adams, Ellis H. Born, Gary C. Smith, Jr..
United States Patent |
3,898,917 |
Adams , et al. |
August 12, 1975 |
Variable displacement fluid translating device
Abstract
An axial piston type fluid energy translating device has fluid
passages in the pistons, shoes, swash plate and cam member to
conduct fluid from the high pressure port to pockets on the back of
the cam member adjacent the cam support. The high pressure fluid in
the pockets counter-balances the force applied to the swash plate
and cam member by the pistons exposed to high pressure fluid.
Inventors: |
Adams; Cecil E. (Columbus,
OH), Born; Ellis H. (Columbus, OH), Smith, Jr.; Gary
C. (Columbus, OH) |
Assignee: |
Abex Corporation (New York,
NY)
|
Family
ID: |
23740146 |
Appl.
No.: |
05/438,311 |
Filed: |
January 31, 1974 |
Current U.S.
Class: |
91/488;
91/489 |
Current CPC
Class: |
F01B
3/0073 (20130101) |
Current International
Class: |
F01B
3/00 (20060101); F04b 001/00 () |
Field of
Search: |
;91/485,486,487,488,499 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Freeh; William L.
Assistant Examiner: LaPointe; G. P.
Attorney, Agent or Firm: Baker, Jr.; Thomas S. Greenlee;
David A.
Claims
Having thus described and shown an embodiment of the invention,
what is desired to secure by Letters Patent of the United States
is:
1. A variable displacement fluid energy translating device
comprising: a body; a barrel rotatably mounted within the body; a
plurality of cylinders formed in the barrel; a piston within each
cylinder; a cam support in the body; a cam member mounted on the
cam support and pivotable relative to the support; a swash plate
having a top surface and a bottom surface and mounted on the cam
member; a shoe pivotably attached to each piston adapted to slide
on the top surface of the swash plate and reciprocate the piston
within a cylinder when the barrel is rotated; means for pivoting
the cam member from a position causing maximum fluid flow in one
direction through the translating device to a position causing
maximum fluid flow in another direction; a bore in each piston for
conducting fluid under pressure in the cylinder through each piston
to its shoe; a second bore in each shoe which feeds fluid from the
piston through the shoe to a space between the bottom of the shoe
and the top surface of the swash plate to hydraulically balance the
shoe; a plurality of apertures in the swash plate for conducting
fluid from the bottom of each shoe through the swash plate; a first
collector port for collecting fluid under pressure from some of the
swash plate apertures when the device is causing fluid flow in one
direction, a second collector port for collecting fluid under
pressure from other of the swash plate apertures when the device is
causing fluid flow in the other direction, the first and second
collector ports being isolated from one another, a third bore in
the cam member for conducting fluid from the first collector port
through the cam member; a first pocket on the back of the cam
member connected to the third bore for receiving the fluid from the
first collector port; a fourth bore in the cam member for
conducting fluid from the second collector port through the cam
member; a second pocket on the back of the cam member connected to
the fourth bore for receiving fluid from the second collector port;
wherein the fluid under pressure in one of the first and second
pockets substantially reduces the friction between the cam member
and the cam support and applies a force on the cam member which
resists the force applied by the pistons on the swash plate.
2. The variable displacement fluid energy translating device
recited in claim 1, including restrictor means positioned between
the swash plate apertures and the collector ports to limit the
amount of pressure fluid that flows out of uncovered swash plate
apertures from the collector ports and to maintain the hydraulic
balance on the shoes.
3. A variable displacement fluid energy translating device
comprising: a body; a barrel rotatably mounted within the body; a
plurality of cylinders formed in the barrel; a piston within each
cylinder; a cam support in the body; a cam member mounted on the
cam support to form a bearing pivotable relative to the support; a
swash plate having a top surface and a bottom surface and mounted
on the cam member; a shoe pivotably attached to each piston and
slideable on the top surface of the swash plate to reciprocate the
pistons within the cylinders when the barrel is rotated; means for
pivoting the cam member from a position of minimum displacement of
the translating device to a position of maximum displacement of the
translating device; a bore in each piston for conducting fluid
under pressure in the cylinder through each piston to its shoe; a
second bore in each shoe which feeds fluid from the piston through
the shoe to a space between the bottom of the shoe and the top
surface of the swash plate to provide pressure fluid beneath the
shoe to substantially hydraulically balance the shoe in opposition
to the thrust of the piston; a plurality of apertures in the swash
plate for sequentially conducting fluid from the bottom of each
shoe through the swash plate; a collector port; fluid restrictor
means connecting the swash plate apertures and the collector port
and limiting the rate of fluid flow from an uncovered aperture to
maintain pressure fluid beneath each shoe; a third bore in the cam
member for conducting fluid from the collector port through the cam
member; a pocket on the back of the cam member for receiving the
fluid from the third bore to lubricate the bearing surfaces between
the cam support and cam member wherein the fluid in the pocket
applies a counter-acting force on the cam member which resists the
force applied by the pistons and shoes on the swash plate.
4. The variable displacement fluid translating device recited in
claim 3 wherein the fluid restrictor means comprises a plurality of
shallow grooves formed on the bottom surface of the swash plate and
the shallow grooves are angled with respect to the apertures in the
swash plate.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The instant invention relates to a variable displacement fluid
translating device of the axial piston type and more particularly
to a means for counterbalancing and lubricating a cam member of
such a device.
2. Description of the Prior Art
A common type of variable displacement fluid translating device
such as an axial piston pump or motor has a rotating barrel with a
plurality of axially aligned cylinders. A piston connected at one
end by a shoe to an angled swash plate is received in each of the
cylinders and reciprocates as the barrel is rotated and the shoe
slides along the swash plate. The stroke of the piston is
controlled by the angularity of the swash plate and determines the
volume of fluid displaced by the fluid translating device
hereinafter referred to as a pump.
In one form of pump, the swash plate is supported by a cam member
which pivots in a cam support about an axis perpendicular to the
rotational axis of the barrel in order to change the volume of
fluid displaced by the pump. During operation of the pump the
cylinders and pistons in the barrel alternately connect with low
and high pressure ports. As the pistons are exposed to the high
pressure port, a large force is transmitted from the fluid through
the pistons and shoes to the cam member. This large force becomes
troublesome when it is desired to pivot the cam member in order to
change the displacement of the pump. The force causes a great deal
of friction between the cam member and the cam support which must
be overcome before the cam member can pivot.
One means of reducing the friction between the cam member and its
support is to coat one of the surfaces with a material which has a
low coefficient of friction. However, it has been found that coated
surfaces erode after heavy use and friction between the cam member
and the cam support begins to increase.
Another means for reducing the friction between the cam member and
the cam support is to connect fluid in the high pressure port with
the space between the cam member and the cam support. In U.S. Pat.
No. 3,682,044, an exterior hydraulic line is run from the high
pressure port to a compensator block which connects the high
pressure fluid with passages leading to holes in the cam support
which holes communicate with the cam member. The effect of this
high pressure fluid is to counterbalance some of the force applied
by the pistons on the cam member and to lubricate the contacting
cam member and cam support surfaces to reduce the friction between
the surfaces and thereby reduce the force required to pivot the cam
member relative to the cam support.
A disadvantage of connecting high pressure fluid to apertures
positioned in the cam support is that the fluid is not always
communicated to the point of maximum force between the cam member
and the cam support. This is because the forces applied to the cam
member act along a line perpendicular to the face of the cam member
which receives the pistons. As the cam member is pivoted in the cam
support, this force is directed through the cam member and acts on
different portions of the cam support.
It is desirable to supply high pressure counterbalancing fluid
between the cam member and the cam support which is at all times
opposite the force applied to the cam member by the pistons.
SUMMARY OF THE INVENTION
It is an object of this invention to provide a variable
displacement fluid translating device in which the forces applied
by the pistons on the cam member are counterbalanced by a pocket of
high pressure fluid acting opposite the position at which the
pistons are applying the force to the cam member.
It is another object of the instant invention to provide a variable
displacement fluid translating device in which high pressure fluid
is conducted through the pistons, the shoes and the cam member to
pockets on the surface of the cam member adjacent the cam support
in order to reduce the friction between the cam member and
support.
Other objects of the invention will appear hereinafter, the novel
features and combinations being set forth in the claims.
In the variable displacement axial piston pump of the instant
invention, high pressure fluid in the barrel cylinders is fed
through the pistons, the shoes, the swash plate and the cam member
to pockets formed on the back surface of the cam member adjacent
the cam support. The pockets are substantially aligned with the
surfaces on the cam member to which the forces are applied by the
pistons. Feeding the high pressure fluid through passages formed in
the piston, the shoes, the swash plate and the rocker cam
eliminates external hydraulic lines from the high pressure port to
the cam support.
DESCRIPTION OF THE DRAWINGS
FIG. 1 is an axial section of a portion of the fluid energy
translating device of this invention.
FIG. 2 is a view of the flat surface of the cam member adjacent the
swash plate.
FIG. 3 is view of the back surface of the cam member which pivots
within the cam member.
FIG. 4 is a view of the swash plate taken along the line 4--4 on
FIG. 1.
FIG. 5 is a view similar to that of FIG. 4 with the number of
apertures in the swash plate changed.
FIG. 6 is a view similar to that of FIG. 4 with the number of
apertures in the swash plate changed.
FIG. 7 is a view similar to that of FIG. 4 with the number of
apertures in the creep plate changed.
DESCRIPTION OF THE PREFERRED EMBODIMENT
The axial piston pump 10 of the instant invention has a casing
which includes an outer cylindrical body 12 and an end cap 13. The
end cap 13 is attached to the body 12 by fastening means not shown.
The casing forms an internal cavity 15 which houses the operating
mechanism of the pump 10.
A barrel 16 is rotatably mounted in a roller bearing 17 in body 12.
Bearing 17 is located in body 12 by a shoulder 18 and a retaining
ring 19 which is urged against bearing 17 by end cap 13. An oil
seal 20 prevents fluid seepage at the joint between body 12 and end
cap 13.
A prime mover not shown drives barrel 16. The prime mover is
attached to one end of a shaft 22 which is coupled to barrel 16 by
splines 23. Shaft 22 is restrained from moving axially relative to
barrel 16 by a bolt 24 which passes through a spring 25, a retainer
26 and is threaded into shaft 22. Clearance between bolt 24 and
retainer 26 permits limited axial movement of shaft 22 relative to
barrel 16.
Within barrel 16 are formed a plurality of cylinders 28 which are
aligned parallel with the axis of rotation of barrel 16. The
cylinders 28 are equally spaced from each other within barrel 16
and are displaced radially from the axis of rotation an equal
distance. Positioned within each cylinder 28 is a hollow piston
29.
At one end of each piston 29 is a shoe 30 which is attached to a
swash plate 31 by a means of a shoe retainer assembly 32. When
barrel 16 is rotated, the shoes 30 slide over swash plate 31 and
reciprocate the pistons 29 in the cylinders 28 to thereby pump
fluid.
The shoe retainer assembly 32 maintains shoes 30 in contact with
swash plate 31. The assembly 32 comprises a shoe retainer plate 34
which has a plurality of openings 35 which are of sufficient
diameter to pass over a piston 29 and engage a shoulder 36 on each
shoe 30. A bolt 38 draws retainer plate 34 towards swash plate 31
to clamp the shoes 30 therebetween. Bolt 38 passes through a
retainer washer 39, a socket member 41, cam member 37, a spring 44,
a spring retainer 45, and has a castle nut 46 turned on the end
thereof. Spring 44 prevents spring retainer 45 from contacting cam
member 37 and enables retainer plate 34 to move slightly in
response to a high axial force on bolt 38. This allows piston shoes
30 to move away from swash plate 31 slightly and ride on a fluid
cushion therebetween.
Cam member 37 is pivotally mounted in a cam support 50. When cam
member 37 is moved relative to cam support 50, the stroke of the
pistons 29 is changed and therefore the displacement of pump 10 is
changed. One means of pivoting cam member 37 is a double headed
piston 55 which is connected to cam member 37 by means of a
bifurcated arm 52.
When rocker cam 37 is pivoted such that swash plate 31 is
perpendicular to shaft 22, there is no reciprocating movements of
pistons 29 when barrel 16 is rotated and pump 10 is operating at
its minimum fluid displacement when barrel 16 is rotated. When
rocker cam 37 is pivoted such that swash plate 31 is angled its
greatest amount, the pistons 29 move through their greatest stroke
and pump 10 is operating at its maximum fluid displacement when
barrel 16 is rotated.
When barrel 16 is rotated and pump 10 is displacing fluid, the
pistons 29 are alternately exposed to high and low pressure ports
in a port plate 58. The pressure in the high pressure port may be
on the order of several thousand pounds per square inch. This force
in transmitted through the piston 29 and its shoe 30 to the swash
plate 31. The force on the swash plate 31 acts to urge the cam
member 37 against the cam support 50. This creates a large amount
of friction which must be overcome when cam member 37 pivots
relative to cam support 50.
In order to reduce the friction between the cam member 37 and the
cam support 50, high pressure fluid is routed to a pocket 71 in the
rear face 59 of cam member 37 to counterbalance the force applied
to the swash plate 31. Pocket 71 is best seen in FIG. 3.
High pressure fluid flows through bore 61 in piston 29, a bore 62
in shoe 30 and into a cavity 63 adjacent swash plate 31. Swash
plate 31 has a plurality of circumferentially arranged passages 65
extending therethrough as seen in FIGS. 1 and 4 through 7. Each
passage 65 is in communication with a shallow metering groove 66
formed on the bottom side of swash plate 31 adjacent cam member
37.
As seen in FIG. 2, a pair of ports 67 are formed in rocker cam 37
to receive fluid which feeds from the grooves 66. One port 67 is
aligned with the grooves 66 and passages 65 which receive fluid
from pistons exposed to the high pressure port and the other port
67 is aligned with the grooves at 66 and passages 65 which receive
fluid from the pistons exposed to the low pressure port of the
pump.
Since only one pump port at a time will conduct high pressure
fluid, only one port 67 at a time will receive high pressure
fluid.
A bore 70 extending from the top surface 68 of rocker cam 37 to the
rear face 59 conducts fluid in the port 67 to the pocket 71. When
the high pressure fluid collects in pocket 71 it resists the force
applied to swash plate 31 by pistons 29 as they are exposed to the
high pressure port. The fluid in pocket 71 also lubricates the face
57 on cam support 50 and face 59 on cam member 37 to reduce the
friction therebetween.
Since pocket 71 is formed in face 59 on the movable cam member 37,
the high pressure fluid is acting at a point directly opposite
where force from the high pressure fluid is being applied by
pistons 29 to the swash plate 31 or any angular position of cam
member 37 in cam support 50.
High pressure fluid is normally fed from the shoes 30 to the
passages 65 in grooves 66 to a port 67. However, when a passage 65
in the swash plate 31 is uncovered, by rotation of the shoes 30
fluid under pressure in the port 67 will leak back through grooves
66 to the uncovered passages 65. Since the passages 65 are only
uncovered for a short time, only a small amount of fluid will flow
back therethrough. The amount of fluid flowing back through is
further reduced because the cross sectional area of a groove 66 is
much smaller than that of a passage 65. The small grooves 66 also
prevent a large amount of fluid from flowing from the cavities 63
under shoes 30 which would drain the fluid required to provide a
fluid film between the shoes 30 and the creep plate 31.
It is important that high fluid pressure in port 67 be maintained
in order to maintain the pressure of the counterbalancing fluid in
the pocket 71. This is only possible if at any moment the majority
of the passages 65 which connect to a port 67 are being fed fluid
at high pressure or are blocked. Consequently, spacing of the
passages 65 is critical.
Refering to FIG. 4, it has been found that it is undesirable to
have the number of passages 65 equal to the number of pistons 29 in
the pump 10 or equal to any multiple thereof. With this number of
passages 65 it is possible that all of the passages 65 could be
uncovered at one time and consequently no high pressure fluid would
be supplied to port 67. FIG. 5 shows that with a number of passages
65 equal to double the number of pistons 29 that at times half of
the passages 65 would be uncovered, and consequently, a majority of
passages 65 would not be feeding high pressure fluid to the port
67.
FIG. 6 shows a creep plate 31 which has eight passages 65 and FIG.
7 shows a creep plate 31 which has twelve passages 65. When these
creep plates 31 are used with a pump having seven pistons 29, and
shoes 30 there are more passages 65 feeding high pressure fluid or
blocking the escape of this fluid from port 67 than there are
passages open and providing a means of escape to the high pressure
fluid.
In FIG. 7, it can be seen that passages 65 are equally spaced from
each other and distance along the arc of the circle on which all
passages 65 lie between the farthest outside edges of two adjacent
passages 65 is less than the outside diameter of a shoe 30.
Consequently, a single shoe 30 may overlie two passages 65.
Obviously, those skilled in the art may make various changes in the
details and arrangements of parts without departing from the spirit
and sculp of the invention as it is defined by the claims hereto
appended. Applicant, therefore, wishes not to be restricted to the
precise construction hereindisclosed.
* * * * *