U.S. patent number 3,808,950 [Application Number 05/305,408] was granted by the patent office on 1974-05-07 for flow-control arrangements in axial-cylinder pumps.
This patent grant is currently assigned to Plessey Handel Und Investments A.G.. Invention is credited to Anthony Roger Davies.
United States Patent |
3,808,950 |
Davies |
May 7, 1974 |
FLOW-CONTROL ARRANGEMENTS IN AXIAL-CYLINDER PUMPS
Abstract
A fluid-tight seal between each cylinder bore in the barrel of a
swash-plate pump and the corresponding port bore in a port plate
rotating with the barrel is established by a sleeve, which is
accommodated in aligned counterbores of the two bores, provided at
the mutually adjacent end faces of the barrel and port plate, and
which is sealed in each of these counter bores by a separate
compressed O-ring seal, common rotation of the port plate with the
barrel being ensured by means independent of the sleeves. The
sleeve has sufficient play in the counter bores to allow for slight
angular displacement between the respective end faces of the
cylinder barrel and the stationary valve face of, for example, a
valve plate. Preferably the O-rings are accommodated in annular
recesses at each of the two ends of the sleeve and are compressed
axially between washers resting respectively against the bottom
shoulders of the two counter bores so that the resilience of the
O-rings provides an axial thrust force urging the port plate into
contact with the valve plate.
Inventors: |
Davies; Anthony Roger (Swindon,
EN) |
Assignee: |
Plessey Handel Und Investments
A.G. (Zurich, CH)
|
Family
ID: |
10465548 |
Appl.
No.: |
05/305,408 |
Filed: |
November 10, 1972 |
Foreign Application Priority Data
|
|
|
|
|
Nov 13, 1971 [GB] |
|
|
52842/71 |
|
Current U.S.
Class: |
91/487 |
Current CPC
Class: |
F04B
1/2035 (20130101) |
Current International
Class: |
F04B
1/20 (20060101); F01b 013/04 () |
Field of
Search: |
;91/486,487,504-506 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Freeh; William L.
Attorney, Agent or Firm: Scrivener Parker Scrivener &
Clarke
Claims
1. An axial-cylinder pump comprising a pump housing, a cylinder
barrel mounted in said housing for rotation about an axis of the
barrel and having a plurality of cylinder bores extending parallel
to said axis at equal radial distances therefrom, a piston in each
cylinder, piston-actuating means operable during rotation of the
barrel to produce periodic reciprocation of each piston in its
associated cylinder, a port plate arranged coaxially with the
barrel for common rotation therewith and having one end face
adjacent to but slightly spaced axially from, one end face of the
barrel and a second, oppositely directed face, said port plate
having port bores, one for each cylinder and each communicating at
said one face of the port plate with its associated cylinder and
terminating at said second face of the port plate in a port for
periodic alternate communication, as the barrel rotates, with ports
in a valve face provided in the housing, said barrel having
communication bores respectively communicating with each cylinder,
and each port of the port plate having a communication bore aligned
with one of said communication bores of the barrel, a sealing
sleeve coaxially accommodated in each communication bore of the
barrel and the aligned communication bore of the port plate so as
to extend simultaneously in both said communication bores, with
radial play in each of said communication bores to permit slight
angular movement of the axis of each sleeve relative to the axis of
each of said aligned communication bores, each sleeve having in its
outer circumferential surface two circumferential recesses
respectively facing the walls of the communication bores of the
barrel and of the port plate, two resiliently compressed sealing
rings for each sleeve respectively accommodated in said two
recesses to ensure a fluid-tight seal of the sleeve in the
communication bore in question notwithstanding the said radial
play, and coupling means, independent of said sleeves, ensuring
common rotation of
2. An axial-cylinder pump as claimed in claim 1, wherein said
communication bores are formed as counterbores terminating in a
shoulder, each of the said recesses of each sleeve being open at
the side adjacent to the nearest end of the sleeve, the sealing
member in each recess being resiliently compressed between the
other side of the recess and said shoulder of the counterbore
accommodating said sealing member as well as between the bottom of
the recess and the circumference of the counterbore so as to exert,
through the intermediary of the sleeve, an axial force tending to
move the port plate away from the cylinder barrel and into
3. An axial-piston pump as claimed in claim 2, including an annular
abutment plate supported on, and extending in a radial direction,
the shoulder formed by the counterbore in the barrel.
Description
This invention relates to axial-cylinder pumps of the kind,
thereinafter called the kind specified, in which a number of
cylinders are arranged in a so-called cylinder barrel which is
mounted for rotation about its axis in a pump housing with the
cylinder bores extending substantially parallel to the axis of
rotation and being spaced at equal radii round the latter and
generally uniformly distributed round the axis, and in which the
rotation of the barrel relative to the housing is utilised for
producing periodic reciprocation of a piston in each cylinder for
each revolution of the barrel, and in which furthermore control of
the flow between each cylinder and a high-pressure and a
low-pressure port respectively in accordance with the direction of
movement of the piston is achieved by co-operation of a port,
communicating with each cylinder and arranged in an end face of the
barrel, with high-pressure and low-pressure ports in the stationary
housing which, by means of mutually sliding sealing surfaces,
respectively associated with the barrel and housing, are placed, by
the rotation of the barrel, in alternate communication with each
cylinder port. In axial-cylinder swash-plate pumps of the kind
specified, the actuation of the pistons is achieved by co-operation
of an extension of each piston with the surface of a track which is
stationary in the housing, and which is inclined to a plane
perpendicular to the axis of rotation in accordance with the
desired stroke of the pistons. The term "pump," when used in the
present specification, is intended, unless the context otherwise
requires, to be broad enough to include a machine whether it is to
be operated to displace fluid when mechanically driven (pumps in
the narrower sense) or for use to produce mechanical power when
actuated by fluid pressure (operation as a fluid-pressure
motor).
In order to maintain reliable seal of the sliding surfaces utilised
to establish, in an axial-cylinder pump of the kind specified, the
alternate connections of each cylinder port with the stationary
ports irrespective of minor errors of angular alignment, -- and
such minor errors, even if not present due to manufacturing
inaccuracies, may be produced in operation due to distribution of
hydraulic pressure forces acting in the gap, however small, between
the co-operating sliding surfaces, -- it has already been proposed
to arrange the ports associated with each cylinder in a so-called
port plate which is connected with the cylinder barrel for common
rotation with it, but is free to carry out a small amount of axial
and tilting movement relative to the barrel, and according to that
proposal, sealing connection between each cylinder bore and the
associated port passage in the port plate is maintained by the
provision of sleeve members which project with one of their ends
into an extension of the cylinder bore and are sealed therein by a
compressible ring accommodated in a circumferential groove in the
outer surface of the sleeve to resiliently maintain sealing
connection while permitting slight tilting movement of the sleeve
in the bore, while the other end of the sleeve is arranged to form
an end-surface seal against the adjacent surface of the port plate
with a view to maintaining an effective seal at that surface
irrespective of slight displacements of the end surface on the
adjacent surface of the port plate.
The present invention has for an object to avoid the necessity of
providing, in order to minimise leakage losses across the end face
of the sleeve, such a sliding end-surface seal and thus the
necessity of maintaining high axial contact pressure which results
in the transmission of an undesirable force to the port plate.
Another object is to provide an axial-cylinder pump having a port
plate, rotatable with the cylinder barrel, which is capable of
reliable operation under conditions of relatively large angular
displacement of the axis of the cylinder barrel relative to the
axis of the port plate.
According to the present invention fluid-tight connection between
each cylinder and its port in the port plate is established by a
sleeve which extends into substantially aligned bores coaxial with
the cylinder in the cylinder barrel and with its port in the port
plate respectively, in each of which bores the sleeve is capable of
a small amount of axial and swivel movement; the port plate is
coupled for common rotation with the cylinder barrel independently
of the presence of these sleeves, and the sleeve is sealed in each
of these bores by a sealing ring of resiliently compressible
material, which is compressed in a circumferential groove or
shoulder portion of one of the co-operating circumferential wall
surfaces of the sleeve and bore so that it maintains, due to its
resiliently compressed state, sealing contact with the other of the
said co-operating surfaces. Preferably each sealing ring is
accommodated in an annular chamber formed within the bore by an
outwardly projecting circumferential shoulder determining a
reduced-diameter portion of the sleeve near the adjacent end
thereof, and is compressed between the face of this annular
shoulder and an opposing face formed or suported by the cylinder
barrel and port plate respectively, so that the resilient
compression of each sealing ring is utilised, in addition to its
use for maintaining circumferential seal in the appropriate bore,
for also maintaining some axial sealing force between the sealing
face of the port plate and the co-operating stationary face which
contains the high-pressure and low-pressure ports of the pump
housing.
In order that the invention may be more readily understood one,
form of swash-plate pump incorporating the present invention will
now be described in more detail with reference to the accompanying
drawing, in which
FIG. 1 is an elevation of the pump in section through the axis of
the cylinder barrel, taken in the direction of maximum inclination
of the swash-plate surface to the face of the port plate,
FIG. 2 is a scrap section drawn to a larger scale and shows details
of the arrangement of one of the sealing sleeves, and
FIG. 3 is a plan view of part of the port plate with a thrust
washer.
Referring now to the drawing, a so-called cylinder barrel 2 is
mounted for rotation about its axis in a housing 1. The barrel 2 is
connected for common rotation with a shaft 3, which is supported in
the housing 1 by bearings 4 and 5. The latter of these is a ball
bearing of a kind capable of transmitting axial thrust as well as
radial forces, and the shaft 3 is provided with a flange 6 which
co-operates with an end face of the cylinder barrel 2 to transmit
axial thrust from the latter to the pump housing 1 through a
further flange 6a resting against the ball bearing 5. The cylinder
barrel 2 is provided with a number of cylinder bores 7 uniformly
distributed round the axis of the shaft 3 at equal distances
therefrom and extending substantially parallel to the shaft. Each
cylinder bore contains a piston 8 having a ball-ended extension 8a
which, in a well-known way, co-operates with a track surface on a
so-called swash plate 9 through the medium of a so-called slipper
10, a separate slipper 10 being provided on the extension of each
piston member 8 for sliding co-operation with the track surface 11
of the swash-plate 9. This surface is inclined to a plane at right
angles to the axis of the shaft 3 so that, during each revolution
of the cylinder barrel 2, each piston, if its slipper 10 is
maintained in contact with the surface 11, will perform one
reciprocation in its cylinder. To maintain such contact, the swash
plate 9 is equipped with a retainer ring 12 which co-operates with
a shoulder 13 of each slipper 10.
To provide alternate connection of each cylinder with the
high-pressure and low-pressure ports of the pump, port passages 14
and 15 of the pump housing 1 are continued in a so-called valve
plate 16 to form the ports proper in the valve plate 16 of which
the surface that faces the end of the cylinder barrel is highly
finished, and a so-called port plate 17, having a similarly
finished surface for co-operation with this surface of the valve
plate 16, is provided with an individual cylinder port 18 for each
cylinder bore 7 of the cylinder barrel 2. This port plate 17 is
coupled to the shaft 3 so as to rotate jointly with the barrel 2
but is slightly spaced axially from this barrel to leave a narrow
gap 19, and a small amount of plate is also provided between the
central bore 17a of the port plate and the shaft 3, to allow the
lower end face 2a of the barrel 2 to assume a slight angle of
inclination to the adjacent end face of the port plate 17 without
interfering with the surface contact between the port plate 17 and
valve plate 16.
A substantially leak-free connection between each cylinder bore 7
and its associated port 18 in the port plate 17 is however assured
by the interposition, between the cylinder barrel 2 and the port
plate 17, of a connector sleeve 20 for each cylinder as will be
described further below. A force, produced by hydraulic pressure
and tending to hold the port plate 17 in contact with the valve
plate 16, is provided by making the ports 18 in the port-plate
kidney-shaped so as to be substantially narrower in the radial
direction of the barrel than the diameter of the cylinder bores 7
and counterbore 21, and by confining the area of which the
distributed pressure of leakage fluid acts between the contacting
sealing surfaces of the valve plate 16 and port plate 17, to a
relatively narrow land 27 surrounding each of the ports 8. This is
achieved by the provision in the end face of the port plate 17 of
drained recesses 25, 26 which encircle this land.
Each connector sleeve 20 is accommodated for part of its length in
a cylindrical counterbore 21 which is provided in the port plate 17
to continue the port 18 axially through the surface facing the
cylinder barrel 2, and whose diameter is substantially larger than
the width of the port 18 transversely of its direction of revolving
movement about the barrel axis. The other end of the sleeve 20 is
accommodated in a counterbore 7a at the adjacent end of the
associated cylinder bore 7 of the cylinder barrel, this
counter-bore being separated from the cylinder bore 7 proper by an
annular shoulder 22, and a thrust washer 29 is preferably
interposed between the shoulder 22 and the sleeve 20 as described
further below. The dimensions of the sleeve 20 are such as to leave
some axial clearance between the ends of the sleeve 20 and the
bottom of the counter-bore 21 and/or shoulder 22 or thrust washer
at the top of the counter-bore 7a, and to leave also some radial
clearance at the circumference of the sleeve 20, thus allowing the
sleeve 20 to accommodate angular displacement of the barrel 2
relative to the port plate 17 in the manner above indicated. In
order to maintain nevertheless the desired fluid-tight seal of the
connection between the cylinder bore 7 and the port 18 in the port
plate 17, two seals are formed in the counter-bores 21 and 7a
respectively by O-rings 23 and 24 of rubber or other resiliently
compressible material. These O-rings are accommodated in suitable
annular recesses of the sleeve 20, which respectively face the wall
of the counter-bore 21 in the port plate 17. and the wall of the
sleeve-accommodation counterbore 7a of the cylinder bore 7. The
O-rings are arranged to be compressed in their cross-section during
the assembly of the device, so as to be applied to the wall of the
said bores with sufficient force to ensure a liquid-tight seal.
Preferably the recesses accommodating the O-rings 23 and 24 are
open at the end faces of the sleeve 20 as illustrated, and the
O-rings 23 and 24 being so dimensioned in their cross-section as to
be not only compressed in the radial direction of the sleeve 20 but
to be also compressed in the longitudinal direction of the latter,
between the shoulder forming the end face of the recess
accommodating each O-ring and the shoulder 22 or thrust-washer 29
which restrains the axial movement of this O-ring towards the
cylinder bore 7. With this arrangement the O-rings 23 and 24, in
addition to their sealing function, also act as thrust springs to
provide a resilient force applying the end face of the port plate
17 to the co-operating surface of the valve plate 16 independently
of any hydraulic pressure.
In order to minimise flow restriction, particularly during the
charming of the cylinders through the low-pressure inlet port 15 of
the pump housing, the length 18a of each port 18 of the port plate
17 in the direction of its movement round the barrel axis is
approximately equal to the diameter of the cylinder bore 7, as will
be seen more clearly in FIG. 2. In order to provide nevertheless
adequate shoulder surface areas at the end 18b of each port 18 to
retain the O-rings 23 and 24 compressed in the axial direction of
the cylinders as well as in a radial direction, the shoulder formed
by the counter-bore 21 is used to support a substantially rigid
thrust washer 28 of a radial width just sifficient to provide such
adequate shoulder surface for the O-ring 24 while the diameter of
its central aperture is at least approximately equal to the
diameter of the axial passage 20a of the sleeve 20 so as to be
clear of the port 18 except for the above-mentioned end areas
18b.
A further thrust washer 29, whose central aperture is likewise
equal to or somewhat larger in diameter than that of the said axial
passage 20a, is similarly supported against a narrow shoulder
formed between the cylinder bore 7 and its counterbore 7a so as to
provide, notwithstanding the small difference between the diameters
of the bore 7 and counterbore 7a, an adequate support surface for
the O-ring 23 at the other end of the sleeve 20. This arrangement
makes it possible to keep the excess in diameter of the
counterbores 7a in the cylinder barrel 2 over the diameter of the
cylinder bore 7 at a minimum, thus minimising the hydrostatic
thrust force which acts on the shoulder 22 between the bore 7 and
counterbore 7a of the cylinder barrel 2 to urge the barrel away
from the valve plate 16, and which must be taken-up by the bearing
5.
Various features of the illustrated embodiment may be varied
without exceeding the scope of the invention. Thus, when the
resilience of one, or both of the O-rings is not required for the
provision of an axial thrust force urging the port plate into
contact with the valve plate, the thrust ring adjacent to that
O-ring, or both thrust rings, may be formed integral with the
sleeve 20, so that the sleeve will butt against the shoulder 22
and/or the bottom of the bore 21, the O-ring in question being
accommodated in a groove of the thus modified sleeve.
Furthermore, the port plate 17, instead of being driven by a shaft
connection as described, could be driven from the cylinder barrel
2, for example, by means of suitably arranged dowels.
* * * * *