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Publication numberUS3680312 A
Publication typeGrant
Publication dateAug 1, 1972
Filing dateOct 9, 1970
Priority dateOct 10, 1969
Also published asDE1951234A1, DE1951234B2
Publication numberUS 3680312 A, US 3680312A, US-A-3680312, US3680312 A, US3680312A
InventorsFranz Forster
Original AssigneeLinde Ag
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Hydrostatic machine
US 3680312 A
A hydrostatic machine, e.g. a hydrostatic pump or hydrostatic motor operating in a closed fluid circuit and having a housing into which leakage of the hydraulic medium can occur, is provided with check valves communicating between the housing and the main ports to enable leakage fluid to pass directly into the main hydraulic circuit.
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Description  (OCR text may contain errors)

[ 51 Aug. 1, 1972 United States Patent Forster 3,143,859 8/1964 Thoma..... ...........60/52 US UX AAR fififi II 000 6 ..t 1 .r e wm wHM 588 666 99 9 H 938 256 243 826 079 333 m m Cuu EmMn N m m a CM G M n,

o m C m numb Aa me fiLW Rm a n D m Y w m HmA P M 7 Primary Examiner-Edgar W. Geoghegan Attorney-Karl F. Ross Appl. No.: 79,532

[22] Filed:

[57] ABSTRACT A hydrostatic machine, e.g. a hydrostatic pump or [30] Foreign Application Priority Data Oct. 10, 1969 Germany.............P 19 51 234.6 hydrostatic motor p i g a closed fluid circuit and having a housing into which leakage of the hydraulic medium can occur, is provided with check [52] US. Cl. ..............60/53 A, 60/52 US, 60/DIG. 5,

60/51 51 Int. Cl. 39/02, Fl6h 39/10 f mmumcatmg heme? d [58] Field of Search.....60/53 A, 52 US, DIG. 5, 53 R mam P0rts to enable leakage mud to P duectly the main hydraulic circuit.

9 Claim, 5 Drawing Figures References Cited UNITED STATES PATENTS 2,597,050 5/1952 Audemar...................60/51UX EP'A'TENTEDms' 1 m2 sum 1 0F 4 Franz Forsfer 1 VENTOR FIG.

PATE'NTEDAIIB- I 1912 3.680.312

sum 2 us 4 50; FIG. 2

INIIII llllllllilllillll llllillm 51d 1 Q I (Q 11 II I! O I H526 X I 610 flair 570 I y I\ -50:

t(@::f) %fiii:::/

II/ Y Franz Forsfer f 1 INVENTOR. 504 520a 513 I FIG. 5

Attorney ms F W? SHEET 3 BF 4 Franz Fors'rer INVENTOR.

Attom e y saw u or 4 Franz F0 rsfer INVENTOR.

A (Ross Attorney 1 HYDROSTATIC MACHINE FIELD OF THE INVENTION My present invention relates to hydraulic machines and, more particularly, to hydrostatic machines operating in a closed fluid circuit.

BACKGROUND OF THE INVENTION Hydrostatic machines, e.g. hydrostatic pumps and motors, generally are provided with a closed circuit and a pair of main ports connected with a hydraulic load and serving as discharge or intake ports, depending upon the sense of operation of the machine. Among the important hydrostatic machines of this class are the socalled axial-piston pumps and axial-piston motors which serve, respectively, to displace the hydrostatic fluid under the drive of a power source, e.g. an intemalcombustion engine or an electric motor and/or may be driven by hydraulic fluid pressure to operate, in turn, a mechanical member such as the output shaft. Axialpiston devices and the principles involved therein are described in FLUID POWER, US. Government Printing Office, 1966, at pages 109-112 and pages 199 and following, respectively.

For the most part, an axial-piston pump may comprise a rotary cylinder barrel provided with a plurality of angularly equispaced cylinder bores successively communicating with a pair of kidney-shaped fluid-distribution apertures on a fluid-distribution surface against which the cylinder barrel is held under axial pressure. The pistons within the cylinders are reciprocated by virtue of rotation of the barrel and the fact that the pistons bear upon a control surface which is inclined to the axes of rotation of the barrel so that during about half of each rotation the pistons are urged inwardly while the pistons are able to move outwardly during the remainder of each rotation.

Inward displacement of the pistons, of course, corresponds to a reduction in the volume of the chamber behind the piston to expel fluid in the form of a hydraulic medium through one kidney-shaped aperture while outward movement of the piston expands the chamber to draw the hydraulic medium into the cylinder bore from the other kidney-shaped aperture. The kidneyshaped apertures, of course, are connected to the discharge and intake ports of the hydraulic machine, respectively, depending upon the angle and direction of tilt of the control surface, the displacement of the pump and the function of the main port (as high-pressure or low-pressure port) can be established. The pump shaft may be connected to the control surface to drive the latter and may also be coupled with the barrel via means as described, for example, in the commonly assigned copending application Ser. No. 68,254 filed Aug. 31, 70 by Walter HEYL. A hydrostatic motor operating in accordance with the same principles, will generally comprise a cylinder barrel having a surface perpendicular to its axis of rotation abuting a fluid-distribution surface whose arcuate apertures communicate with the individual cylinder bores opening at this surface. The pistons may bear against an inclined control surface and are coupled with an output shaft via the latter so that fluid entering through one of the apertures forces the piston successively outwardly to drive the barrel and, consequently, rotate the shaft. Inclination of the control surface in this case, determines the speed of the shaft and the torque delivered to any load which may be coupled therewith.

It is not uncommon to interconnect the discharge port of the pump with the intake side of the motor and the outlet side of the motor with the intake side of the pump by suitable conduits and thereby create a hydrostatic drive or transmission in which the transmission ratio between the input shaft of the pump and the output shaft of the motor is established by the inclination of the barrel axes of the hydrostatic machines to the axis of the respective shaft. Such transmissions may be wholly contained in a common housing or may be mounted remote from one another so that they can be connected by relatively longlines. One advantage of the hydrostatic transmission is precisely the possibility of providing the hydrostatic pump in the vicinity of a prime mover or other energy source, while the hydrostatic motors are mounted directly adjacent the load driven thereby. Transmissions of this nature have been found to be particularly suitable in vehicular applications wherein the prime mover is an internal-combustion engine and the load is the vehicle wheel. Of course, a number of hydrostatic motors can be connected to a single pump or a number of pumps may be provided to service a single hydrostatic motor. In general, however, it is found to be advantageous to provide each hydrostatic pump with a hydrostatic motor in a closed fluid path.

It should be understood. that the term closed fluid path is intended herein to refer to a system in which the pump is connected directly to the load, i.e. each of the conduits communicating with the ports of the pump run to the corresponding ports of the motor. While one of the conduits may be operated as a high-pressure transmission line while the other conduit is at low pressure, the hydrostatic machines are generally reversible to interchange the functions of these lines. Furthermore, both machines may be provided in a closed housing so that the entire transmission network and fluid supply is contained within this housing from which only the input and output shafts emerge. In closed circulating paths of the character described, it is necessary to hold the low-pressure side at a predetermined pressure level and an auxiliary pump and/or a pressure-regulating valve may be used to this end.

It will be appreciated that effective operation of the axial-piston pump or axial-piston motor is accompanied and in fact may require some leakage of the hydraulic medium from the system, e. g. at the fluid-distribution surfaces of a valve plate and the rotating cylinder drum, respectively. When a closed circulating path was required, it has been necessary in some priorart devices to provide a further conduit between the pump and load to convey the leakage fluid from one hydrostatic machine to the other. This is, of course, a significant disadvantage when the pump is greatly removed from the motor and when complex mechanisms are interposed between them. In an excavating machine, for example, the hydrostatic pump may be mounted upon a chassis carrying a turntable which, in turn, is provided with the excavating scoops and like devices. When the turntable is used, it rotates relatively to the chassis. Hence hydrostatic motors carried by the turntable must be connected through a rotating seal with the hydrostatic pump and the need for an additional conduit between the hydrostatic motor and the hydrostatic pump complicates such systems to a further extent. It will be appreciated that conduits for the indicated purposes must be capable of withstanding pressure and the use of an additional conduit involves increasing complexities because of the associated seals.

In open hydraulic circuits, moreover, i.e. those using a collecting reservoir into which fluid flows in a pressureless state, it is common to connect the leakagefluid conduit to the reservoir so that the fluid returns to the power cycle, the leakage path being pressureless. It is also known to provide, in such systems (open fluidcirculating path), pumps which are disposed'directly in the reservoir and leakage can occur directly into the reservoir. These systems make use of a relatively large housing for the pump and possible pressurization of the fluid therein to prevent cavitation at the inlet side of the pump. In all cases, however, techniques which have been found to be satisfactory for handling the leakage fluid of the open hydraulic circuit, i.e. those using fluid reservoirs, have not been found to be practical or satisfactory in closed fluid circuits while the need for added leakage-fluid conduits renders earlier closed systems expensive and complex.

OBJECTS OF THE INVENTION It is the principal object of the present invention to provide an improved hydrostatic machine arrangement of the closed-circulation type wherein the aforementioneddisadvantages are obviated.

Another object of my invention is to provide an improved hydrostatic'machine, e.g. axial-piston pump or axial-piston motor, in which the handling of leakage fluids is simplified, which is of lower cost and simpler operation than earlier systems, and which can be used for arrangements such as excavators in which two hydraulic machines are interconnected but separated by means creating sealing difficulties.

SUMMARY OF THE INVENTION The above and other objects of the invention, which will become apparent hereinafter, are attained in a hydraulic machine which comprises a housing, preferably closely surrounding the axial-piston barrel which is connected directly with the low-pressure port of the machine, i.e. the intake port of a hydrostatic pump or the discharge port of a hydrostatic motor, via a check valve designed to permit unidirectional flow of the hydraulic medium from the housing surrounding the barrel into the low-pressure port. The housing sealingly closes the hydrostatic machine and, when the ports of the machine are functionally interchangeable, both of them may be connected with the housing chamber by respective check valves, only the check valve communicating with the low-pressure port being open to permit the pressure differential thereacross to feed the leakage fluid into the low-pressure side. The

high-pressure side, of course, maintains its check valve low-pressure side of the hydrostatic machine, a check valve connecting the interior of the housing with the low-pressure duct, conduit or port, and a hydrostatic machine disposed within this housing and having a leakage path opening from the machine into the housing whereby the leakage medium can traverse the check valve into the low-pressure ducts. A separate leakage-fluid collector is thereby eliminated, the system does not require a separate line between the pump and motor for conducting the leakage fluid and compensating for leakage losses, and only two ducts need bridge the hydrostatic pump and motor. Furthermore, the cooling of the hydrostatic machine is improved by virtue of the fact that there is a continuous circulation of the leakage medium from the machine into the space surrounding the machine and enclosed by the housing, and from the housing into the low-pressure side of the machine.

The present invention is applicable to hydrostatic pumps and motors, the intake of the fonner being the low-pressure side whereas the discharge of the latter is at low pressure. However invention can also apply to more than one hydrostatic machine in a single housing, i.e. a double-pump assembly in which two hydrostatic pumps are provided within a single housing, two hydrostatic drives including a pump and one or more motors, the housing in each case being generally closed. However, it has beenfound that increasing the size of the housing to accommodate more than one hydrostatic machine opens the door to difficulties with respect to maintaining the seal of the housing and it is therefore preferred to provide a housing for each machine which closely surrounds the axial-piston drum thereof. It should be noted that one not only achieves a saving in the cost of a leakage-fluid duct when the present invention is used, but also reduces the complexities of the pump and motor structures themselves since fittings, ports, chambers and like structure associated with the leakage ducts are eliminated as well. It is possible by such simplification of the overall structure to eliminate the tendency of the machine to leak and thereby reduce maintenance and surveillance.

The reduction of the leakage losses from the main closed hydraulic circuit into the housing surrounding the hydrostatic machine is a consequence in part of the high back pressure maintained in the sealed housing and, therefore, prevalent at the outlet side of the leakage path. As a result, no feed pump need be used to compensate for leakage loss in a great many cases and, wherever a feed ptunp is required in a system under the present invention, it may be dimensioned to have a smaller capacity and energy consumption than the feed pumps which have been used heretofore with similar hydraulic machines operating, for example, in closed circuits with pressurelesshousings or the like.

When no feed pump is required, I have found it to be advantageous to provide, at one or more locations along the closed hydraulic path, equalization reservoirs or hydropneumatic accumulators adapted to deliver,

while maintaining the pressure in the housing, fluid to the latter to compensate for the leakage losses from the main hydraulic circuit. Such accumulators may be of the type described at pages 86 89 of FLUID POWER. cited earlier. The accumulator, which is maintained at the predetermined pressure within the sealed housing,

compensates for changes in the volume of fluid available in themain circulating path as a result of thermal expansion and contraction of the fluid and the conduits containingv same, elastic yieldability of the conduit walls, etc.

When ahydropneumatic accumulator is employed, I have found it advantageous after a period determined by experience, e.g. a thousand operating hours, to charge the accumulator and restore the pressure therein. Of course, the accumulator should only be provided. at the low-pressure sideof the, closed circulation pathand, when the. hydraulic machine is reversible so that the ports alternate in function between high-pressure. andilow-pressure ports, reversing-valve means is used in accordance. with the invention to connect the low-pressure side, with the accumulator at all times. Two such accumulators may, of course, be provided and connectedwith thesides of the hydraulic network by cutoff valve means so that the accumulator currently at the high-pressure. side is blocked .while the other accumulator is rendered effective. Furthermore, when a pair of interconnected hydrostatic machines are employed, the. accumulator can communicate directly with the interior'of one of the machine housings or the common housing of both machines to maintain the pressure in the low-pressure side of the network substantially constant-indirectly.

When a feed pump is provided, i.e. when the hydrostatic machine is provided with a pump designed to deliver the-hydraulic medium to the closed fluid path to compensatefor leakage losses, a secondary circulation is established between the housing chamber of one machine preferably the motor and the low-pressure line thereof. A cooling system can be provided in the latter case at the discharge side of the feed pump. The cooler may be a conventional radiator built onto the housing of the apparatus or other conventional heat-dissipating device. Hence the interior of the housing is constantly rinsed with fresh cool hydraulic medium and the machine is able to operate with increasing efficiency.

Accordingto still another feature of this invention, the hydrostatic machine forms part of a hydraulic transmission driven by an internal-combustion engine and the working fluid of the hydrostatic drive is also the lubricant for the. internal combustion engine. The feed pump and cooling pump can thereby constitute the means for maintaining the predetermined pressure within the housing, the means for cooling the latter, and the means for lubricating the engine.

DESCRIPTION OF THE DRAWING The above and other objects, features and advantages -of the present invention will become more readily apparent from the following description, reference being made to the accompanying drawing in which:

FIG. 1 is an axial cross-sectional view through an embodiment of a hydrostatic machine according to the invention; FIG. 2 is a side-elevational view, partly in axial section and partly in diagrammatic form, illustrating another embodiment of the invention wherein the hydrostatic machine employs a feed pump;

FIG. 3 is a view similar to FIG. 2 of a hydrostatic transmission according to the invention;

FIG. 4 is a view similar to FIG. 1 illustrating how the invention is applied to a double-pump assembly; and

FIG. 5 is an elevational view diagrammatically illustrating the application of the invention to another hydrostatic transmission having a single housing.

SPECIFIC DESCRIPTION In FIG. 1 I have shown a hydrostatic machine having a shaft 1 which may serve as the input shaft of the hydrostatic pump and which is joumaled in a pair of axially spaced bearings 5 and 6 of a housing 3, 4 interconnected at 3a. The shaft 1 carries a cylinder drum 2 provided with a plurality of angularly equispaced axially extending cylinder bores 7, each slidably receiving a piston 8 shiftable into and out of the cylinder bore 7 parallel to its own axis and the axis of the shaft 1. Each of the pistons 8 is provided with a swivel head or ball 8a which is received swivelably within a shoe plate 9 of annular configuration, slidably bearing against a control disk 10 whose surface 10a is inclined at the angle a to the axis A of the shaft. Spring means (not shown) may be provided to ensure that the pistons 8 and the shoe 9 seats firmly against the control surface 10a at all operating speeds of the rotary machine.

The housing 3, 4 comprises a bell-shaped member 3 having a neck 3b in which the bearing 5 is received and which is formed with a lip-type seal capable of maintaining a subatmospheric pressure in a chamber 16 surrounding the cylinder barrel 2. The latter is provided with apertures 7a which open at a valve surface 2a bearing against the opposing surface of a valve or distributing plate 15 composed of low-friction material, e.g. bronze, seated against the plate 4. The plate 15 is provided with a pair of arcuate apertures 15a and 15b, respectively registering with several of the apertures 7 a as the barrel 2 rotates relative to the plate 15. Such arcuate apertures are disclosed in the aforementioned publication. Each of the apertures 15a and 15b registers, in turn, with a respective connecting passage 13 or 14 communicating, in turn, with the ports 11 and 12 to which suitable conduit means may be connected for joining the hydrostatic machine of FIG. 1 in a closed hydraulic circuit. A typical circuit is that illustrated in FIG. 3. When port 11 forms the high-pressure side of the machine, port 12 represents the low-pressure side and vice versa. The pressure at the low-pressure side may be maintained constant by a feed pump or pressure-regulation valve interconnecting the high and lowpressure sides. The low-pressure side preferably is held at about 6 to 8 atmospheres gauge. The same pressure is maintained by seal 23 within the housing. When the system is a hydrostatic motor, the discharge is at this pressure while, when the machine is a hydrostatic pump, the supply or intake is at this pressure.

The interior 16 of the housing communicates via respective bores 17 and 18, formed directly in plate 4, with respective check valves 20 and compartments l9 and 21 operating, respectively, into the passages 13 and 14 mentioned earlier. The check valves 20 are poled, oriented and constructed to permit unidirectional flow of fluid from the housing into the low-pressure conduit or branch when a pressure differential in favor of such flow is established and to block reverse flow of fluid under any circumstances. Since reverse flow is blocked when the pressure difl'erentialfavors an outflow from the network into the chamber 16, whenever the operat- I ing high pressure is maintained in one of the networks, the corresponding check valve blocks flow therethrough and only the other check valve can operate, this only when the pressure within the housing exceeds the pressure within the low-pressure side as indicated.

The shaft 1 may be coupled to a prime mover, e. g. an electric motor or an internal combustion engine for use of the machine as a pump, or may be connected to a load such as the driving wheels of an automotive vehicle having a hydrostatic transmission. In the mode of operation of the machine as a pump, the barrel 2 is rotatably entrained by the shaft 1 while the pistons 8 ride with the shoe v9 along the control surface 10a which is inclined to the axis of rotation of the barrel as noted earlier. As the pistons 8 are shifted between their fully extended position and a fully retracted position, they vary the size of the chamber 7 behind the piston and thereby draw fluid through one port and force it out through .the other in a repetitive intake/discharge cycle. When the machine is operated as a motor, hydraulic fluid is delivered by a hydrostatic pump at one port to drive the pistons outwardly as the barrel swings into registry with that port, the fluid then passing at low pressure into the discharge side for return to the pump. In either case, one of the ports 11 or 12 will be a high-pressure port while the other is the low-pressure port.

When port 11 is under high pressure and port 12 is under low pressure, the fluid in line 13 is likewise at an elevated pressure to bias the check valve 19 into a closed position. Fluid from the chamber 16 cannot enter the closed hydraulic network via line ,17. However, the normal pressure in the housing chamber 16 is 6 to 8 atmospheres (gauge) and sufflces, when thepressure drops at the low-pressure duct 14 and port 12, to bleed the leakage fluid from the chamber 16 into the hydraulic line 14 for return to the main circulating path. The fluid within the chamber 16 in part derives from leakage at the control surfaces 2a. When the control surface 10a is adjusted to vary the functions of the ports or the sense of rotation is altered, only the check valve associated with the low-pressure side will be operative. The high-pressure check valve will invariably be closed.

In FIG. 2, I show a hydrostatic machine according to the invention which is constituted as a pump and embodies many of the features already described in connection with FIG. 1. In this embodiment, the shaft 101, extending out of the, housing portion 103 is connected with a drive means such as an inlet combustion engine or electric motor. The shaft 10l is provided with an extension. 25 beyond the bearing 106 running to a feed pump 26, the latter being bolted onto the housing portion 104 forming the fluid-distribution ports 111 and 112 as well as ducts 113 and 114 as previously described.

The intake line 27 of the pump 26 is fed from a reservoir 28 while the pressure side of the pump26 is connected via line 29 to the using compartment 116 through the wall 103 thereof, preferably at the bottom of the wall. A return line 31 communicates with the compartment 1 16 at the upper side thereof via a fitting which is provided with a check valve 32 allowing unidirectional flowing from the housing to the reservoir 28. Valve 32 is provided with a strong spring 32a so that it simultaneously constitutes a pressure-regulating valve maintaining an adjustable pressure in the compartment 1 16 at about 6 to 8 atmospheres. In thiscase, the reservoir 28 can be open to the atmosphere and can constitute a heat exchanger or heat-dissipating cooler directly. As an alternative, the reservoir 28 may be closed to maintain a given pressure within the system and the cooler may be provided as a separate heat exchanger or radiator in a fluid circuit with the pump 1 26. The pump 26, consequently, circulates fresh fluid through the interior of the housing constantly with the advantages already set forth. In general, the machine of FIG. 2 operates in the manner previously described in FIG. 1 when the barrel 102 is rotated by shaft 101 to shift the pistons 107 in the cylinder bores 108 of the closed hydraulic circuit and permit the check valve or 122 associated with the low-pressure side to connect the respective passage 113 or 114 with the interior of .the housing.

The hydrostatic drive illustrated in FIG. 3 comprise in accordance with the usual practice, a hydrostatic pump whose shaft 201 is connected with an internal combustion engine and whose hydrostatic motor has its shaft 301 connected with a load. The shafts 201 and 301 are rotatably connected with the cylinder barrels 202, 302 whose pistons 208, 308 are axially shiftable, via inclined control surfaces not shown, within the cylinder bores 207, 307 to displace hydrostatic fluid along a closed path inter-connecting the, ports 211 and 311 via a line 33 and the ports 212, 312 via a line 34. It will be appreciated that the lines 33 and 34 may be relatively long when the pump and the motor are to be separated by some distance or can be eliminated when a single support block is provided in place of the separate fluid distribution plates 204, 304. The

remainder of the system, including the fluid-distribution antifriction plates 215, 315 the ports 217 and 317 connected to the low-pressure side of the network and the check valves 220, 320 and222, 322 is, of course, identical with the corresponding parts of the system of FIG. 1. In addition, a pressure-equalization reservoir 36, in which a compressed gas is maintained in the compartment 36a to form a yieldable cushion for the membrane 36b connected with line 35 and the chamber 216. A valve 360 serves to permit recharging of the accumulator. With expansion of the fluid within the transmission as a result of heating, there is a volume increase which is taken up by the accumulator 36 with compression of the gas cushion therein. Should there be a leak from the housing or an elastic yielding of the ducts from a housing and portions thereof, additional fluid is delivered by the accumulator. No separate feed pump is necessary.

In FIG. 4, I show a system wherein a housing 403, 404 is common to a pair of cylinder drums 402, with respective shafts 401 driven via gears 401a from a gear 40lb on the crankshaft 4010 of an automotive vehicle or like installation using a double pump aggregate. Since separate closed hydraulic networks may be provided with the low-pressure ports 412 at the same pressure and the high-pressure ports 411 at respective elevated pressures, a check valve 420 is provided to connect both ports 412 with the interior 416 of the BEST AVAILABLE COPY housing. The other check valves 422 for the high-pressure side are provided as previously described.

FIG. shows a system wherein the cylinder drums 502 and 602 of the hydrostatic pump and hydrostatic motor are mounted in a common housing 503 and have input and output shafts 501 and 601 respectively connected to a source of rotary movement and a load. The control member 510 is here shown to be pivotal via lever 510' to adjust the displacement of the pump and a similar means may be provided for tilting the control plate 610. A single valve block 504 is here used with the intake side of the duct 514 connected with the check valve 520. Pressure within the system may be controlled by a regulating valve 650 connecting the high and low pressure lines or by a feed pump 526 driven by gearing 561 from the pump shaft 501. The major distinction between the system of FIG. 5 and that of FIG. 4 is the single housing for the barrels of both the pump and motor of this latter system.

In FIG. 5, I also show a distributing valve 520a by which the check valve 520 and the duct associated pressure corresponding substantially to that of said low-pressure passage; and a duct wholly within said housing constituting the sole leakage-fluid path therefrom and connecting said low-pressure passage with said chamber, and a check valve in said duct for unidirectional flow of fluid between said chamber and said low-pressure passage and blocking reverse flow of therewith may be switched between the current lowpressure line 514 and the high-pressure line 513 when the hydraulic machines are reversed as described earlier. in this case only a single check valve need be used. The valve 520a may be coupled as represented by the dot-dash line 52% with lever 510 to effect automatically the change-over.

I claim:

1. A hydraulic system comprising a hydrostatic pump and a hydrostatic motor constituting hydrostatic machines; means connecting said machines in a closed fluid-circulating path and including a high-pressure passage and a low-pressure passage; a pressure-retentive housing surrounding at least one of said machines and-forming a chamber maintainable at an elevated fluid through said duct between said low-pressure passage and said chamber.

2. The hydraulic system defined in. claim 1 wherein a respective duct connects each of said passages with said chamber and is provided with a respective check valvepermitting unidirectional flow of fluid from the chamber into said passages.

3. The hydraulic system defined in claim 1, further comprising distributing valve means for selectively connecting said duct with one of said passages.

4. The hydraulic system defined in claim 1, further comprising a feed pump connected with said chamber for circulating fluid therethrough.

5. The hydraulic system defined in claim 4, further comprising a heat-dissipating cooler in a hydraulic circuit with said feed pump.

6. The hydraulic system defined in claim 1 wherein both said machines are provided within said housing.

s l l h in fi "fl 1% hyil i ulic system defined in claim 1, further comprising means for maintaining the pressure within said chamber at a level of substantially 6 to 8 atmospheres gauge.

9. The hydraulic system defined in claim 1 wherein said housing encloses a pair of hydrostatic pumps, coupled together in a double-pump aggregate.

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US2597050 *Jul 11, 1947May 20, 1952Olaer MarineHydraulic transmission for reproducing mechanical motions at remote points
US3143859 *Mar 7, 1963Aug 11, 1964Dowty Hydraulic Units LtdHydraulic apparatus
US3208222 *Jul 18, 1963Sep 28, 1965Atlas Industriewagen G M B HBattery operated industrial truck
US3372545 *Feb 7, 1966Mar 12, 1968Dowty Technical Dev LtdHydraulic apparatus
US3396536 *Aug 8, 1966Aug 13, 1968Cessna Aircraft CoHydraulic transmission
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US4821936 *Sep 21, 1987Apr 18, 1989Mobil Oil CorporationHydraulic index drive system
US4987796 *Jun 12, 1989Jan 29, 1991Tecumseh Products CompanyInternal reservoir-defining body for permitting oil expansion within a hydrostatic transmission housing
US5001901 *Oct 4, 1988Mar 26, 1991Sundstrand CorporationHydraulic fluid circuit for full case hydraulic unit
US5094078 *Jul 30, 1990Mar 10, 1992Honda Giken Kogyo Kabushiki KaishaHydraulic transmission for motor vehicle
US5146748 *Aug 16, 1990Sep 15, 1992Kanzaki Kokyukoki Mfg. Co., Ltd.Axle driving apparatus
US5235810 *Sep 28, 1992Aug 17, 1993Tecumseh Products CompanyConduit valve providing wide neutral in a hydrostatic transmission
US5419130 *Jan 13, 1994May 30, 1995Hydromatik GmbhHydrostatic machine with drain oil discharge
US5440878 *Aug 27, 1992Aug 15, 1995Vernon E. GleasmanVariable hydraulic machine
US5473964 *Feb 7, 1994Dec 12, 1995Kanzaki Kokyukoki Mfg. Co., Ltd.Axle driving apparatus
US5598748 *May 30, 1995Feb 4, 1997Kanzaki Kokyukoki Mfg. Co., Ltd.Axle driving apparatus
US5636555 *May 24, 1995Jun 10, 1997Kanzaki Kokyukoki Mfg. Co. Ltd.Axle driving apparatus
US5647249 *May 24, 1995Jul 15, 1997Kanzaki Kokyukoki Mfg. Co. Ltd.Axle driving apparatus
US5655417 *May 24, 1995Aug 12, 1997Kanzaki Kokyukoki Mfg. Co. Ltd.Hydraulic transaxle
US5664465 *May 24, 1995Sep 9, 1997Kanzaki Kokyukoki Mfg. Co., Ltd.Axle driving apparatus
US5694816 *May 24, 1995Dec 9, 1997Kanzaki Kokyukoki Mfg. Co., Ltd.Axle driving apparatus
US5752417 *Jan 2, 1997May 19, 1998Kanzaki Kokyukoki Mfg. Co. Ltd.Axle driving apparatus
US5782142 *Apr 12, 1996Jul 21, 1998Tuff Torq CorporationAxle driving apparatus
US5950500 *Sep 5, 1997Sep 14, 1999Kanzaki Kokyukoki Mfg. Co., Ltd.Axle driving apparatus
US6443263 *Sep 5, 2000Sep 3, 2002Honda Giken Kogyo Kabushiki KaishaOil tank for an internal combustion engine
US6491118 *Nov 20, 2000Dec 10, 2002Deere & CompanyHydrostatic system with charge flow monitoring
US6672843Apr 8, 2002Jan 6, 2004Hydro-Gear Limited PartnershipDual pump apparatus comprising dual drive shafts and auxiliary pump
US6889595 *Aug 20, 2003May 10, 2005Hydro-Gear Limited PartnershipPump
US6938718Dec 29, 1999Sep 6, 2005Kanzaki Kokyukoki Mfg. Co., Ltd.Axle driving apparatus
US6953327Mar 11, 2003Oct 11, 2005Hydro-Gear Limited PartnershipDual pump
US7000388 *Mar 15, 2004Feb 21, 2006Honda Motor Co., Ltd.Hydraulic continuously variable transmission
US7082762Jan 24, 2005Aug 1, 2006Hydro-Gear Limited PartnershipPump
US7178336Nov 29, 2005Feb 20, 2007Hydro-Gear Limited PartnershipPump
US7229256Apr 20, 2005Jun 12, 2007Hydro-Gear Limited PartnershipDual pump transmission
US7263829 *Dec 22, 2006Sep 4, 2007Hydro-Gear Limited PartnershipPump
US7320577Apr 7, 2005Jan 22, 2008Hydro-Gear Limited PartnershipDual pump transmission
US7409829 *Sep 11, 2006Aug 12, 2008Kanzaki Kokyukoki Mfg. Co., Ltd.Pump unit
US7418819 *Aug 16, 2006Sep 2, 2008Kanzaki Kokyukoki Mfg. Co., LtdPump unit
US7516615Aug 24, 2007Apr 14, 2009Hydro-Gear Limited PartnershipPump
US7566207Jun 19, 2007Jul 28, 2009Hydro-Gear Limited PartnershipDual pump transmission
US7677038Jan 19, 2007Mar 16, 2010Kanzaki Kokyukoki Mfg. Co., Ltd.Pump unit
US7788919Jul 29, 2008Sep 7, 2010Kanzaki Kokyukoki Mfg. Co., Ltd.Pump unit
US7806667Jun 8, 2007Oct 5, 2010Hydro-Gear Limited PartnershipDual pump
US8272315Sep 3, 2010Sep 25, 2012Hydro-Gear Limited PartnershipDual pump
EP1378662A1 *Jul 5, 2002Jan 7, 2004Bieri Hydraulik AgHydraulic axial piston pump
WO1998011345A1 *Sep 2, 1997Mar 19, 1998Meiller FahrzeugeHydraulic pump and hydraulic engine
U.S. Classification60/455, 60/912, 60/489
International ClassificationF03C1/06, F04B1/20, F16H39/14, F03C1/253, F03C1/26, F16H61/40
Cooperative ClassificationF04B1/2064, F16H39/14, F16H61/40, Y10S60/912
European ClassificationF04B1/20C5, F16H39/14, F16H61/40