WO1996000838A1 - Axialkolbenmaschine mit einem kühlkreislauf für die zylinder und kolben - Google Patents
Axialkolbenmaschine mit einem kühlkreislauf für die zylinder und kolben Download PDFInfo
- Publication number
- WO1996000838A1 WO1996000838A1 PCT/EP1995/002180 EP9502180W WO9600838A1 WO 1996000838 A1 WO1996000838 A1 WO 1996000838A1 EP 9502180 W EP9502180 W EP 9502180W WO 9600838 A1 WO9600838 A1 WO 9600838A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- axial piston
- piston machine
- cooling
- machine according
- cylinders
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
- F01B3/0052—Cylinder barrel
Definitions
- the invention relates to an axial piston machine according to the preamble of claim 1.
- an axial piston machine in which, for the purpose of avoiding the metallic contact between the piston and cylinder on the circumference of each cylinder or the associated piston, pressure pockets are formed symmetrically and each have a throttle and an axial through bore in the piston with the Working space of the cylinder are connected.
- the piston is lubricated and relieved of hydrostatic pressure by the high pressure oil flowing into the pressure pockets from the work area during the compression stroke and thus guided centrically in the cylinder without the risk of canting.
- the amount of oil required for this hydrostatic relief is missing in the working circuit of the axial piston machine and thus leads to a reduction in the efficiency of the same.
- This cooling takes place by means of a cooling circuit which is connected to the leakage chamber, that is to say is completely separate from the working circuit of the axial piston machine and in this way does not impair its efficiency.
- the leakage fluid in the leakage space has its strongest cooling effect in the start-up phase, when the risk of piston seizure is greatest, because in this phase its temperature roughly corresponds to the ambient room temperature.
- the leakage fluid in the leakage chamber is heated to higher temperatures during continuous operation of the axial piston machine, its cooling effect is sufficient due to the temperature difference corresponding to the pressure difference compared to the fluid under high pressure in the working circuit, to counter the considerably reduced risk of piston seizure due to the piston lubrication used in the meantime.
- This cooling device for cooling the leakage fluid in the cooling circuit.
- This cooling device can be designed in the form of a further leakage fluid receiving space in a connection block attached to the housing and containing the pressure and suction channel of the axial piston machine.
- the cooling areas are preferably designed as annular spaces which surround the cylinders with a small radial distance.
- the cooling areas are advantageous to design the cooling areas as annular grooves in the cylinder walls, so that the leakage oil serves not only for cooling but also for additional lubrication of the pistons.
- the arrangement and the number of annular spaces or annular grooves can be matched to the respective operating conditions of the axial piston machine.
- a distributor channel and in the case of the ring groove a distributor groove can be connected to this upper cooling area, which surrounds the assigned cylinder essentially in a spiral and opens out on the end face of the cylinder drum facing the lifting disk.
- a cooling area can also be used, which is formed in the area of the cylinder drum above the piston crown with the piston at the bottom dead center.
- At least one upper and one lower cooling area are preferably provided, which can be connected to one another by a distributor channel or a distributor groove.
- the leakage oil flow can be maintained through an inlet channel opening into one of the cooling areas and an outlet channel opening out of the respective other cooling area.
- the suction channel of the axial piston machine is connected to the cooling circuit via a dosing egg.
- the forced flow via the throttle improves the cooling properties because relatively cool oil always flows in from the suction channel.
- Figure 1 as a first embodiment of an axial piston machine in axial section with a cooling circuit for cooling the
- Figure 2 as a second embodiment of the axial piston machine according to Figure 1 in axial section with a cooling circuit in a second embodiment
- Figure 3 as a third embodiment of the axial piston machine according to Figure 1 in axial section with a cooling circuit in a third embodiment
- Figure 4 as a fourth embodiment of the axial piston machine of Figure 1 in axial section with a cooling circuit in a fourth embodiment
- FIG. 5 shows an axial section in a schematic representation along the line V - V in FIG. 4, which shows the forces acting on the pistons of the axial piston machine according to FIGS. 1 to 4;
- FIG. 6 shows the axial piston machine as the fifth exemplary embodiment
- Figure 1 in axial section with a cooling circuit which is connected to the suction channel by means of a throttle.
- the axial piston machine shown in FIGS. 1 to 4 is designed in a swashplate construction with an adjustable displacement volume and a flow direction and, in a known manner, comprises, as known components, a hollow cylindrical housing 1 with an end open at the end (upper end in FIG. 1), one attached to the housing 1, the one of which open end closing connection block 2, a lifting or swash plate 3, a control body 4, a drive shaft 5, a cylinder drum 6 and a cooling circuit 7.1 to 7.4 according to the invention.
- the swash plate 3 is designed as a so-called swivel cradle with a semi-cylindrical cross-section (compare FIG. 5) and is supported with two bearing surfaces that run parallel to the swivel direction at a mutual distance, with hydrostatic relief on two correspondingly shaped bearing shells 8, which lie on the inner surface of the connection block 2 opposite Housing end wall 9 are attached.
- the hydrostatic relief takes place in a known manner via pressure pockets 10 which are formed in the bearing shells 8 and are supplied with pressure medium via connections 11.
- the control body 4 is fastened to the inner surface of the connection block 2 facing the housing interior and is provided with two through openings 15 in the form of kidney-shaped control slots which are connected via a pressure channel 16D or suction channel 16S in the connection block 2 to a pressure and suction line, not shown are.
- the pressure channel 16D has a smaller flow cross section than the suction channel 16S.
- the spherical control surface of the control body 4 facing the housing interior serves as a bearing surface for the cylinder drum 6.
- the drive shaft 5 protrudes through a through hole in the housing end wall 9 into the housing 1 and is by means of a bearing 17 in this through hole and by means of a further bearing 18 in a narrower bore section of an enlarged blind hole 19 in the connection block 2 and a closer to this Bore section adjacent region of a central through bore 20 in the control body 4 rotatably mounted.
- the drive shaft 5 passes through a central through hole 21 in the swash plate 3, the diameter of which is dimensioned according to the largest swivel deflection of the swash plate 3, as well as a central through hole in the cylinder drum 6 with two bore sections.
- One of these bore sections is formed in a sleeve-shaped extension 23 formed on the cylinder drum 6, over which the end face 22 facing the swash plate 3 protrudes, via which the cylinder drum 6 is connected in a rotationally fixed manner to the drive shaft 5 by means of a keyway connection 24.
- the remaining bore section is conical; it tapers from its cross-section of largest diameter near the first bore section to its cross-section of smallest diameter near the end face or bearing surface of the cylinder drum 6 which is in contact with the control body 4.
- the annular space defined by the drive shaft 5 and this conical bore section is designated by the reference number 25 designated.
- the cylinder drum 6 has generally axially extending, stepped cylinder bores 26, which are arranged uniformly on a partial circle coaxial with the drive shaft axis, directly on the cylinder drum end face 22 and on the cylinder drum bearing surface facing the control body 4 via outlet channels 27 on the same partial circle as that Open the control slots.
- a bushing 28 is inserted into each of the larger diameter cylinder bore sections opening directly on the cylinder drum end face 22.
- the cylinder bores 26 including the liners 28 are referred to here as cylinders.
- Pistons 29, which are displaceably arranged within these cylinders 26, 28, are provided at their ends facing the swash plate 3 with ball heads 30 which are mounted in slide shoes 31 and, via these, on an annular slide plate 32 fastened to the swash plate 5 are stored hydrostatically.
- Each sliding block 31 is provided on its sliding surface facing the sliding plate 32 with a pressure pocket, not shown, which is connected via a through hole 33 in the sliding block 31 to a stepped axial through channel 34 in the piston 29 and in this way with the piston 5 in the cylinder bore 26 delimited working space of the cylinder is connected.
- a throttle is formed in each axial through channel 34 in the area of the associated ball head 30.
- a holding-down device 36 which is arranged axially displaceably on the drive shaft 5 by means of the keyway connection 24 and is acted upon by a spring 35 in the direction of the swash plate 3, holds the sliding shoes 31 in contact with 10 the sliding disk 32.
- the space not taken up in the interior of the housing by the components 3 to 6 etc. contained therein serves as a leakage space 37 which, during operation of the axial piston machine, passes through all the gaps, such as between the 15 cylinders 26, 28 and the pistons 29, for the control body 4 and the cylinder drum 6, the swash plate 3 and the sliding plate 32 and the bearing shells 8, etc., absorbs leaking fluid.
- the function of the axial piston machine described above is generally known 20 and is limited to the essential in the description below when used as a pump.
- the axial piston machine is designed for operation with oil as a fluid.
- the cylinder drum 6 together with the piston 29 is rotated via the drive shaft 5.
- Swash plate 3 is vertical. This normal force is broken down into a piston force Fj j and a radial or transverse force Fq in the spherical piston 30.
- the shear force Fq acts in
- Piston 29 in metallic contact with the liner 28, whereby very high surface pressures can occur, which are the cause of correspondingly high frictional forces and thus heating at the contact points.
- conventional axial piston machines without the cooling circuit 7.1 to 7.4 according to the invention in particular during the start-up phase, in which there is still insufficient piston lubrication by the pressure oil in the cylinders 26, 28, to eat the pistons 29 and thus to damage them and the cylinders 26 , 28 lead.
- the cooling circuit 7.1 to 7.4 is connected to the leakage space 37 and comprises the conical annular space 25 (so-called leakage fluid receiving space), the through hole 20 in the control body 4, the blind bore 19 (so-called further leakage fluid reception space), a connecting this with the leakage space 37
- Connection line 38 which opens out into a circumferential groove 39 in the inner surface of the connection block 2, and cooling areas associated with the cylinders 26, 28, which are connected circumferentially and are connected to the conical annular space 25 via inlet channels 40 and via outlet channels 41 to the cylindrical boundary surface 42 of the cylinder drum 6 open into the leakage space 37.
- All inlet channels 40 open into the conical annular space 25 at its cross-section with the largest diameter and, like all outlet channels 41, run essentially radially through the cylinder drum 6.
- each cylinder 26, 28 is assigned a cooling area in the form of an annular space 43, which is designed as a circumferential groove in the wall of the cylinder bore section of larger diameter and is covered by the liner 28.
- the annular space 43 extends from near the opening area of the cylinder bore 26 over approximately two thirds of the length thereof in the direction of the opening channels 27 and thus represents an upper cooling area assigned to the top dead center position of the piston 29 Inlet channel 40 and an outlet channel 41 open approximately centrally in the annular space 43 and run coaxially to one another.
- Annular spaces 43 leak oil flowing around the bushings 28 transported into the leak space 37. Since the pressure difference of a maximum of almost 400 bar between the high-pressure oil delivered by the axial piston machine and the leak oil in the leakage space 37 corresponds to a temperature difference of about 7 ° C per 100 bar, the critical points of the metallic contact between the piston 29 and the Bushings 28 effectively cooled and thus prevents the pistons 29 from seizing. During continuous operation of the axial piston machine, the heating leakage oil in the leakage space 37 is cooled as it flows through the blind bore 19 in the connection block 2, since this is exposed to the room temperature and is therefore cooler than the leakage oil in the leakage space 37.
- the leakage oil in the cooling circuit 7.1 can be kept at correspondingly low temperatures by appropriately designing the connection block 2 and the blind bore 19 and, if appropriate, additionally cooling them by means of a separate coolant.
- the cooling circuit 7.1 serves only as a cooling circuit due to the lack of connection to the cylinders 26, 28 (due to the closed annular spaces 43). Since the above-described axial piston machine is intended for operation with oil, the cooling circuit 7.1 can additionally take on a lubricating function if, for example, the annular spaces 43 are connected to the cylinders 26, 28 via corresponding bores through the bushings 28.
- the axial piston machine equipped with the cooling circuit 7.1 is designed for medium outputs due to the arrangement of the annular spaces 43 in the mouth area of the cylinders 26, 28.
- the cooling circuit 7.2 according to FIG. 2 differs from that according to FIG. 1 with otherwise the same design and cooling function in that its cooling areas have the shape of annular grooves 44 which are formed in the bushings 28 and are open towards the inside of the cylinders 26, 28.
- the axial piston machine equipped with the cooling circuit 7.2 is designed for lower outputs than the axial piston machine according to FIG. 1 due to the smaller axial width of the annular grooves 44 compared to the annular spaces 43 and at the same time takes on additional lubrication of the pistons 29.
- the cooling circuit 7.3 according to FIG. 3 differs from that according to FIG. 2 with otherwise the same construction and function in that a distributor groove 45 is connected to each annular groove 44, which is formed in the bushing 28, surrounding it spirally, and on the end face 22 of the Cylinder drum 6 opens out.
- the range of action of the ring grooves 44 with regard to cooling and lubrication is expanded by the leakage oil flowing out of them via the distributor grooves 45 into the leakage space 37 up to the mouth of the cylinders 26, 28.
- the cooling circuit 7.4 according to FIG. 4 comprises, per cylinder 26, 28, the upper annular space 43 shown in FIG. 1, but with a smaller axial width, and a further, lower annular space 46 of the same dimensions, which is located in the lower end region of the bushing 28, that is to say in the region of the Cylinder 26, 28 is formed above the piston crown 47 with the piston 29 in the bottom dead center position.
- An inlet channel 40 is connected to the upper annular space 43 and an outlet channel 41 is connected to the lower annular space 46.
- a distributor channel 48 is provided which connects the two annular spaces 43, 46 to one another.
- the cooling circuit 7.4 is provided for very high-performance axial piston machines.
- This cooling circuit can be used for high-performance axial piston machines if the annular spaces 43, 46 and possibly the distributor channel 48 are connected to the cylinders 26, 28 via corresponding bores through the bushings 28. The same effect is achieved if the annular spaces 43, 46, the distributor channel 48 and the bores mentioned are replaced by annular grooves and distributor grooves according to FIG. 3.
- FIG. 6 shows the cooling circuit 7.1 already shown in FIG. 1.
- the exemplary embodiment shown in FIG. 6 differs from that according to FIG. 1 in that a through hole 51 is provided between the suction duct 16S and the blind bore 19, which connects the suction duct 16S of the axial piston machine to the cooling circuit 7.1.
- An anti-pulsation throttle 50 is arranged in the bore 51. The fluid of the suction channel 16S, which is under pre-compression, flows into the cooling circuit 7.1 via the anti-pulsation throttle 50, as a result of which leakage losses are compensated for.
- the fluid flowing in via the throttle 50 achieves a certain forced flow in the cooling circuit 7.1, as a result of which the cooling properties of the cooling circuit are improved.
- an effective cooling of the fluid circulated in the cooling circuit 7.1 is achieved by the inflow of the lower-temperature fluid from the suction channel 16S.
- the use of the anti-pulsation throttle 50 results in a reduction in the pressure pulsation in the suction channel 16S, which leads to a considerable reduction in the operating noise.
- the inflow from the suction channel 16S can be arranged at different points on the axial piston machine and can open into different areas of the cooling circuit.
- the arrangement of the throttle 50 in the connection block 2 is particularly advantageous, where it can be integrated in a simple manner between the blind bore 19 and the suction channel 16S.
- the anti-pulsation throttle 50 shown in FIG. 6 can also be used without problems in the exemplary embodiments described above with reference to FIGS. 2 to 4.
- cooling areas are examples and can be changed to suit the respective operating conditions.
- the cooling circuit according to FIG. 4 it is possible to connect both annular spaces or annular grooves to an inlet channel and an outlet channel, respectively, and to omit the distributor channel or the distributor groove.
- the invention can also be implemented in inclined axis machines, since here too the pistons jamming radial forces can occur, due to an inclined position of the pistons or piston rods as a result of deviations between the part circle of the spherical seats in the drive pulley, which appears as an ellipse, and the Pitch circle of the cylinders.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP95921838A EP0767864B1 (de) | 1994-06-30 | 1995-06-07 | Axialkolbenmaschine mit einem kühlkreislauf für die zylinder und kolben |
DE59503183T DE59503183D1 (de) | 1994-06-30 | 1995-06-07 | Axialkolbenmaschine mit einem kühlkreislauf für die zylinder und kolben |
JP50274496A JP3570517B2 (ja) | 1994-06-30 | 1995-06-07 | シリンダおよびピストン用の冷却回路を有するアキシャルピストン機械 |
US08/765,341 US5971717A (en) | 1994-06-30 | 1995-06-07 | Axial piston machine having a cooling circuit for the cylinders and pistons |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DEP4423023.0 | 1994-06-30 | ||
DE4423023A DE4423023C2 (de) | 1994-06-30 | 1994-06-30 | Axialkolbenmaschine mit einem Kühlkreislauf für die Zylinder und Kolben |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1996000838A1 true WO1996000838A1 (de) | 1996-01-11 |
Family
ID=6521964
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1995/002180 WO1996000838A1 (de) | 1994-06-30 | 1995-06-07 | Axialkolbenmaschine mit einem kühlkreislauf für die zylinder und kolben |
Country Status (5)
Country | Link |
---|---|
US (1) | US5971717A (de) |
EP (1) | EP0767864B1 (de) |
JP (1) | JP3570517B2 (de) |
DE (2) | DE4423023C2 (de) |
WO (1) | WO1996000838A1 (de) |
Families Citing this family (33)
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DE19613609C2 (de) * | 1996-04-04 | 2000-02-17 | Brueninghaus Hydromatik Gmbh | Axialkolbenmaschine mit internem Spülkreislauf |
DE19620167C2 (de) * | 1996-05-20 | 1998-11-12 | Brueninghaus Hydromatik Gmbh | Hohlkolben mit radial verschweißtem Deckel |
DE19648319B4 (de) * | 1996-06-18 | 2009-01-02 | Continental Teves Ag & Co. Ohg | Radialkolbenpumpe |
DE19706075C2 (de) | 1997-02-17 | 2001-05-17 | Brueninghaus Hydromatik Gmbh | Kolben für eine hydrostatische Maschine |
EP0943798B1 (de) | 1998-03-16 | 2004-08-18 | Brueninghaus Hydromatik Gmbh | Axialkolbenmaschine mit hydrostatischer Entlastung der Zylinderbohrungen |
DE19815614B4 (de) * | 1998-03-16 | 2005-09-08 | Brueninghaus Hydromatik Gmbh | Axialkolbenmaschine mit hydrostatischer Entlastung der Zylinderbohrungen |
DE19837647C2 (de) * | 1998-08-19 | 2000-06-21 | Brueninghaus Hydromatik Gmbh | Hydrostatische Maschine mit Verjüngung in der Kolbenwand oder der Laufbuchse |
JP2001193639A (ja) * | 2000-01-11 | 2001-07-17 | Toyota Autom Loom Works Ltd | 電動斜板圧縮機 |
EP1225331A3 (de) * | 2001-01-23 | 2003-06-11 | Brueninghaus Hydromatik Gmbh | Zylindertrommel für hydrostatische Axialkolbenmaschinen |
US7073427B2 (en) | 2001-09-19 | 2006-07-11 | Brueninghaus Hydromatik Gmbh | Hydrostatic machine with compensated sleeves |
DE10157248A1 (de) * | 2001-09-19 | 2003-04-10 | Brueninghaus Hydromatik Gmbh | Hydrostatische Maschine mit kompensierten Laufbuchsen |
US6893228B2 (en) * | 2002-11-22 | 2005-05-17 | Caterpillar Inc | Axial piston pump with fluid bearing arrangement |
DE10349318B4 (de) * | 2003-10-23 | 2006-10-05 | Brueninghaus Hydromatik Gmbh | Anschlußplatte einer hydrostatischen Maschine und Verfahren zur Herstellung der Anschlußplatte |
DE10351473B3 (de) | 2003-11-04 | 2005-07-21 | Brueninghaus Hydromatik Gmbh | Axialkolbenmaschine |
US7086225B2 (en) | 2004-02-11 | 2006-08-08 | Haldex Hydraulics Corporation | Control valve supply for rotary hydraulic machine |
DE102006058355A1 (de) * | 2006-03-10 | 2007-09-13 | Brueninghaus Hydromatik Gmbh | Kombi-Pumpengehäuse für mehrere Nenngrößen |
DE102006046128A1 (de) * | 2006-06-02 | 2007-12-06 | Brueninghaus Hydromatik Gmbh | Axialkolbenmaschine mit hydrostatischer Auflage des Niederhalters |
DE102006048411A1 (de) * | 2006-06-02 | 2007-12-06 | Brueninghaus Hydromatik Gmbh | Axialkolbenmaschine mit hydrostatisch gelagertem Wiegenzapfen |
US7765917B2 (en) * | 2007-01-12 | 2010-08-03 | Black & Decker Inc. | Air compressor |
DE102009052608A1 (de) | 2009-11-03 | 2011-05-05 | Robert Bosch Gmbh | Axialkolbenmaschine in Schrägscheibenbauweise |
DE102012006289A1 (de) * | 2012-03-29 | 2013-10-02 | Robert Bosch Gmbh | Hydrostatische Axialkolbenmaschine |
DE102013208439A1 (de) | 2013-05-08 | 2014-11-13 | Robert Bosch Gmbh | Hohlkolben für eine hydrostatische Kolbenmaschine |
US9803660B1 (en) * | 2014-02-04 | 2017-10-31 | Danfoss Power Solutions Inc. | Low friction compact servo piston assembly |
DE102014217143A1 (de) | 2014-08-28 | 2016-03-03 | Robert Bosch Gmbh | Zylindertrommel für eine hydrostatische Axialkolbeneinheit |
DE102014220763A1 (de) * | 2014-10-14 | 2016-04-14 | Robert Bosch Gmbh | Hydrostatische Maschine |
CN105201816B (zh) * | 2015-09-07 | 2017-03-22 | 福州大学 | 一种斜盘式柱塞泵的缸体自冷却结构 |
CN105332875B (zh) * | 2015-11-17 | 2017-12-19 | 四川嘉泉科技有限公司 | 一种多功能水油两用电动泵 |
DE102016114148A1 (de) * | 2016-08-01 | 2018-02-01 | L'orange Gmbh | Hochdruckpumpe, insbesondere zur Kraftstoffeinspritzung |
JP2018076826A (ja) * | 2016-11-10 | 2018-05-17 | 川崎重工業株式会社 | シリンダブロックとそれを備えた斜板形液圧回転装置 |
DE102018205884A1 (de) * | 2018-04-18 | 2019-10-24 | Robert Bosch Gmbh | Axialkolbenmaschine mit Druckentlastung in den Durchtriebsraum |
US11118681B2 (en) * | 2019-04-24 | 2021-09-14 | Purdue Research Foundation | Piston-type positive displacement machine with a pressure-adaptive piston-cylinder interface |
US11621604B2 (en) | 2020-02-16 | 2023-04-04 | Purdue Research Foundation | Integrated electro-hydraulic machine |
DE102021209515A1 (de) * | 2021-08-31 | 2023-03-02 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydrostatische Axialkolbenmaschine mit einem Kühlkreislauf und Servo-hydraulischer Aktuator mit einer hydrostatischen Axialkolbenmaschine und mit einem Kühlkreislauf |
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DE1267985B (de) * | 1964-06-06 | 1968-05-09 | Bosch Gmbh Robert | Laufbuchse fuer Kolbenpumpen |
GB1309746A (en) * | 1969-04-11 | 1973-03-14 | Clerk R C | Axial piston rotary barrel type hydraulic pumps or motors |
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-
1994
- 1994-06-30 DE DE4423023A patent/DE4423023C2/de not_active Expired - Fee Related
-
1995
- 1995-06-07 WO PCT/EP1995/002180 patent/WO1996000838A1/de active IP Right Grant
- 1995-06-07 DE DE59503183T patent/DE59503183D1/de not_active Expired - Lifetime
- 1995-06-07 US US08/765,341 patent/US5971717A/en not_active Expired - Lifetime
- 1995-06-07 JP JP50274496A patent/JP3570517B2/ja not_active Expired - Fee Related
- 1995-06-07 EP EP95921838A patent/EP0767864B1/de not_active Expired - Lifetime
Patent Citations (5)
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DE1403754A1 (de) * | 1960-08-31 | 1969-01-23 | Mini Of Technology | Druckmittelbetaetigte Maschine mit hin- und hergehendem Kolben |
GB1029910A (en) * | 1963-11-29 | 1966-05-18 | Rech Etudes Prod | Lubrication devices |
DE1804529A1 (de) * | 1967-10-30 | 1969-07-03 | Abex Corp | Fluessigkeitsmotor oder Pumpe |
FR1595812A (de) * | 1968-11-28 | 1970-06-15 | ||
EP0041312A1 (de) * | 1980-06-04 | 1981-12-09 | General Signal Corporation | Strahlpumpe zum Kühlen |
Also Published As
Publication number | Publication date |
---|---|
EP0767864B1 (de) | 1998-08-12 |
DE4423023C2 (de) | 1998-07-09 |
US5971717A (en) | 1999-10-26 |
JPH10502148A (ja) | 1998-02-24 |
DE59503183D1 (de) | 1998-09-17 |
DE4423023A1 (de) | 1996-01-04 |
JP3570517B2 (ja) | 2004-09-29 |
EP0767864A1 (de) | 1997-04-16 |
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