EP1046819A2 - Machine hydraulique volumétrique - Google Patents

Machine hydraulique volumétrique Download PDF

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Publication number
EP1046819A2
EP1046819A2 EP00108204A EP00108204A EP1046819A2 EP 1046819 A2 EP1046819 A2 EP 1046819A2 EP 00108204 A EP00108204 A EP 00108204A EP 00108204 A EP00108204 A EP 00108204A EP 1046819 A2 EP1046819 A2 EP 1046819A2
Authority
EP
European Patent Office
Prior art keywords
pressure
connection
piston
control
bore
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP00108204A
Other languages
German (de)
English (en)
Other versions
EP1046819A3 (fr
Inventor
Manfred Unsöld
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP1046819A2 publication Critical patent/EP1046819A2/fr
Publication of EP1046819A3 publication Critical patent/EP1046819A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2564—Plural inflows
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2564—Plural inflows
    • Y10T137/2567—Alternate or successive inflows

Definitions

  • the invention relates to a hydraulic displacement machine, in particular a gear machine, according to the preamble of Claim 1 and one for the control of such Gear valve provided control valve.
  • Gear machines for example gear pumps, are used all used in mobile hydraulics because they are a comparative have a simple structure and relatively light allow high pressures. Another advantage of gear machines lies in the fact that this has a comparatively large speed, Temperature and viscosity range can be used.
  • a gear pump is described in EP 0 445 529 B1 the two gears are rotatably mounted in a housing.
  • the Displacement chambers are meshed with one another Tooth flanks, the housing inner wall and an axial or Pressure plate limited.
  • the latter is pressurized on the back, so that it seals against the gear wheel end faces is held.
  • the one on the back of the printing plate acting pressure can be adjusted via a control device in which an orifice formed by a directional valve and a 3-way pressure compensator work together. This is in the sense an increase in back pressure from downstream pressure the orifice plate and a compression spring and in the sense of a Reduction of the back pressure from the pressure upstream the orifice plate.
  • the pressure compensator connects to this one with a pressure chamber on the back of the printing plate connected control connection to the pressure outlet of the pump or with the tank, creating the sealing gap between the pressure plate and the gear end faces is reduced or enlarged.
  • the pressure medium can directly from the Outflow high pressure side to the low pressure side, so that the volumetric Efficiency of the gear machine can be reduced and thus, for example, the delivery rate of a gear pump depending of the gap width is adjustable. That is, by influencing of the pressure medium pressure acting on the pressure plate exact flow control can be done.
  • the pump housing must be comparatively complex because Space for the consumer-side directional control valve and the pressure compensator must be provided. Furthermore, it must have its own pressure relief valve be provided to limit the maximum pressure.
  • a pump arrangement is shown in US Pat. No. 4,014,630 which a sealing plate on a spring in a contact position to the Conveyor elements is pressed.
  • the spring chamber is via a throttle bore connected to the displacement space of the pump arrangement, so that the pressure plate is also hydraulically in its sealing position is biased.
  • the pressure acting on the pressure plate can are in turn influenced by a control device, via the the pressure medium can be discharged into a tank.
  • a disadvantage of this Construction is that pressure fluid through the throttle bore is withdrawn from the displacement chambers, so that the volumetric Efficiency is reduced. Furthermore, the Slightly close the through hole of the pressure plate so that a appropriate maintenance of the pump assembly is required.
  • the invention has for its object a hydraulic Displacement machine, especially a hydraulic one Gear machine, to create, with minimal jig Adequately accurate flow control is feasible.
  • Another job is a control valve suitable for such a displacement machine create.
  • the displacement machine according to the invention is preferably used as Gear machine executed, the front seal the displacement space is done by a pressure plate, the back is supplied with a control pressure via a control valve.
  • the control valve has a piston through which the volume flow adjustable to the consumer and hydraulic with the pressure plate connected control connection with a pressure connection or a return connection is connectable, so that the pressure on the Back of the pressure plate can be raised or lowered.
  • the piston is designed as a hollow piston, the through hole acts as an orifice plate, so that one end of the piston through the pressure downstream of the orifice and the other face of the piston by the pressure upstream of the orifice is.
  • This control valve is characterized by an extremely compact Structure out, so that the housing of the displacement machine is very can be easily trained.
  • this is done Control and opening of the control connection and the return connection of the control valve over two at an axial distance from each other arranged control edges of the piston, so that the piston with increasing volume flow can be brought into a control position, in the control connection with the pressure connection via the control edges or is connected to the return connection.
  • the piston is advantageously with a further control edge executed, over which with a sufficiently large shift from the Control position a flow section upstream of the orifice bore is connectable to the return port, so that the pressure plate is relieved and quick adaptation to changes in flow rate is possible.
  • the manufacturing engineering effort to manufacture the piston is particularly simple if the orifice plate is through a section of a Through hole of the piston is formed.
  • A can be used to dampen volume flow / pressure fluctuations End portion of the piston with a peripheral wall of the Form a damping gap in the piston-receiving axial bore, by the pressure medium when the piston moves axially must pass through.
  • the rear can the pressure plate either with the pressure upstream or downstream of the orifice hole.
  • the pressure medium is upstream of the throttle cross-section of the orifice bore opening led to the tax connection, while in the latter Fall the pressure medium only after flowing through the orifice hole reaches the control connection through the spring chamber.
  • the invention can be particularly advantageous in an internal gear machine use an eccentrically arranged Ring gear meshes with a driven pinion and the pressure plate the ring gear and the pinion at least in sections on the end face seals.
  • the control valve is radially outside the high pressure range is arranged in the housing.
  • the structure of the housing is particularly compact if the control valve is tangential extending pressure channel is arranged so that the pressure connection opens into the side surface of the housing.
  • the part of the air flowing off when the return port is open Pressure fluid can be returned internally or in a tank.
  • the applicant reserves the right, on the special arrangement of the Control valve in the housing and / or to reduce the opening cross-section the suction opening has its own independent requirements to judge.
  • Fig. 1 shows a circuit diagram of a hydraulic according to the invention Displacement machine, for example as an internal gear pump 1 is executed. Through this pressure medium is over a Suction line 2 sucked out of a tank T, pressurized and via a pressure line 4 to a consumer, for example an actuating cylinder 6 of a CVT transmission (continuous Variable transmission).
  • a Suction line 2 sucked out of a tank T, pressurized and via a pressure line 4 to a consumer, for example an actuating cylinder 6 of a CVT transmission (continuous Variable transmission).
  • the internal gear pump is described in more detail below Design carried out in which the front seal the displacement space via a pressure plate (see Fig. 2 to 4) he follows.
  • the pressure plate is by a spring 26 and a Pressurized medium in the direction of its sealing position, so that the sealing gap by adjusting the pressure on the back of the printing plate is adjustable.
  • the pressure plate has practically the function of the directional valve designated by reference numeral 8 in FIG. 1.
  • Fig. 1 is also located the spring 26, which in practice by a surrounding a pressure field on the back of the printing plate Seal that has spring action is realized. With sufficient Pressure on the back of the pressure plate (directional valve 8 in the blocking position) the displacement space is sealed at the end, so that over the internal gear pump 1 promotes a maximum volume flow is.
  • the control valve assembly 12 has an orifice 14, as in a flow control valve cooperates with a pressure compensator 16.
  • the pressure compensator connects in its spring-loaded basic position 16 the back of the printing plate via a control channel 18 with an upstream of the orifice 14 in the pressure line 4 opening line 20.
  • the counter to the pressure spring of the pressure compensator 16 acting end face is with the pressure in the line 20th acted upon.
  • the other end face is next to the compression spring still via a control line 22 with the pressure downstream of the Measuring aperture 14 applied
  • the pressure compensator 16 is controlled such that a flow rate dependent on the control valve at the control connection 26 regulated pressure is given, for example the contact pressure the pressure plate 8 determined.
  • this control pressure could can also be used for other tasks, so that the Use of the control valve arrangement 12 according to the invention does not depend on the pressing one described in more detail below Pressure plate 8 is limited.
  • the piston of the pressure compensator can be brought into a position in which a flow section upstream of the orifice 14 and the back of the pressure plate 8 are connected to the tank, so that a rapid reduction in flow rate is feasible.
  • 2 to 4 is an embodiment of an internal gear pump 1, in which the aforementioned components, i.e. the internal gear pump 1 with sealing plate 8 and the control valve arrangement 12 are integrated in a common housing.
  • FIG. 2 shows a front view
  • FIG. 3 shows a sectional view Side view
  • Fig. 4 is a partially sectioned rear view the pump.
  • the basic structure of the internal gear pump 1 is already from the prior art, for example from DE 43 22 240 C2 known to the applicant, so that in the following only on the essential components is received.
  • the internal gear pump 1 has a cup-shaped housing 30 with an eccentrically arranged receptacle 32 for a ring gear 34. This meshes with a centrally mounted pinion 36, which is from a the drive shaft 37 passing through the housing 30 is driven. Due to the eccentric arrangement of the ring gear 34 with reference the pinion 36 can be limited by the receptacle 32 Space in a low pressure area 38 and a high pressure area 40 divide.
  • the front end of the high pressure region 40 forms a Pressure plate 42.
  • the teeth dip the ring gear 34 and the pinion 36 into one another, so that between A displacement space is formed for every two teeth face of the pressure plate 42 and the bottom of the receptacle 38 is limited.
  • a filling piece not shown, is arranged, which is supported in the housing via a filler pin 44.
  • the filler lies with its side surfaces on the teeth of the pinion 36 and the ring gear 34, so that there are gaps in the teeth Pressure medium along the filler in the meshing area (High pressure area 40) is performed.
  • the feeding of the Pressure medium in the low pressure area 38 is carried out by a Suction opening 46 in the end face 48 of the housing 30.
  • Das pressurized pressure medium is passed through a pressure opening 50 dissipated in the end face 48.
  • the suction opening 46 and the pressure opening 50 an approximately kidney-shaped cross section, the suction opening is arranged radially further outward than the pressure opening 50 and also has a larger cross-sectional area.
  • Fig. 3 shows a section along the line A-A in Fig. 2. Accordingly the internal gear pump 1 is closed at the end by means of a housing cover 52, which is visible in FIG Flange surface 55 of the housing is screwed on.
  • the housing cover 52 lies with one indicated by two dots in FIG Seal 54 on the pressure plate 42.
  • the seal 54 engages a pressure field, which is described in more detail below Way is pressurized with high pressure. About this pressure field becomes in the axial direction with play between the housing cover 52 and the end faces of the ring gear 34 and the pinion 36 recorded pressure plate 42 in its contact position against the End faces (see Fig. 3) biased.
  • a shaft seal 56 is also arranged.
  • the pinion 36 is rotationally fixed to the drive shaft 37 or in one piece trained with this.
  • the sealing plate surrounds 42 with a bearing eye towards the housing cover 54 extending collar 60 of pinion 36.
  • the filler pin 44 passes through the pressure plate 42.
  • the pressure plate 42 can be moved in the axial direction, so that the sealing gap between the end faces of the gears 34, 36 and the contact surface of the sealing plate 42 is adjustable. This means that if this sealing gap is enlarged, pressure medium can be applied directly flow from high pressure area 40 into low pressure area 38, so that the volumetric efficiency of the internal gear pump 1 is reduced and thus the volume flow delivered can be adjusted by varying the sealing gap.
  • the contact pressure of the sealing plate 42 is controlled by a control valve 62 set.
  • This control valve 62 which acts as a current regulator, is shown in FIG Cartridge design and in a tangential Pressure channel 64 of the housing 30 is used.
  • the pressure channel 64 opens into a stepped pocket 66 in the end face 48 of the housing 30.
  • the pocket 66 extends from the suction opening 50 to a recessed, kidney-shaped section 68, in which the pressure channel 64 opens. That is, the pressure medium can be the pressure opening 50 through the pocket 66 in the kidney-shaped Section 68 and from there into the tangential Coming pressure channel 64, which is practically the pressure connection of Internal gear pump 1 forms.
  • the pressure channel 64 has an abutment shoulder 70 on which the control valve 62 rests in its installation position. According to the representation Fig. 4, the control valve 62 is still at a distance from the contact shoulder 70 so that a return channel 72 is visible, which practically corresponds to the return channel 24 according to FIG. 1
  • this return channel 72 ends approximately radially running recess 74 in the flange 55, that in the peripheral wall the recording 32 opens.
  • control channel 76 (indicated by dashed lines in Fig. 4), which corresponds to the control channel 18 in Fig. 1.
  • the control channel 76 leads to a curved groove 80 in the flange surface 55 of the housing 30.
  • This groove 80 acts with a in FIG Dash-dotted connection channel 82 in the housing cover 52 together, so that pressure medium via the control channel 76, the groove 80 and the connecting channel 82 into that of the seal 54 limited pressure field can be fed to the sealing plate 42nd in the direction of their contact position on the wheels 34, 36.
  • the connecting channel 82 is an angled hole in the housing cover 52 formed, both bore sections of the end facing the housing 30 are drilled here and are arranged at an obtuse angle to each other. This course of the Connection channel 82 is indicated by dash-dotted lines in FIG. 3.
  • Control valve 62 The structure of a first preferred embodiment of the Control valve 62 will now be explained with reference to FIG. 5.
  • the control valve 62 inserted into the pressure channel 64 is of a cartridge design executed and has a sleeve 84, in the axial bore 86 a piston 88 is slidably guided.
  • the right one in Fig. 5 End portion of the axial bore 86 is radial to a damping bore 90 downgraded.
  • the piston arranged in the enlarged part of the axial bore 86 88 has three axially spaced ring collars 92, 94, 96, the Ring collar 92 forms the left end face of the piston 88 in FIG. 5. Following the right (Fig. 5) collar 96 is the piston 88 reset radially. This radially recessed end section 98 dips in sections into the damping bore 90 and forms a damping gap together with this.
  • the piston 88 is in its in FIG. 5 via a compression spring 100 biased basic position shown, the compression spring 100th on the ring end face of the radially stepped part of the Axial bore 86 is supported and on the 30 annular end face of the Ringbundes 96 attacks.
  • the spring chamber 102 is between via the damping gap the damping bore 90 and the end portion 98 with connected to the area downstream of the piston 88.
  • the piston 88 is designed as a hollow piston and has a stepped bore, the right part of which is designed as an orifice bore 104 is.
  • the input and output ports 106 and 108, respectively are through the mouth areas of the axial bore 86 of the sleeve 84 trained.
  • the sleeve has two axially spaced ring grooves 110, 112, one or more of a control connection in the annular groove 112 114 radial bores and in the annular groove 110 radial bores forming a return connection 116 open out.
  • a jacket bore is in the peripheral wall of the piston 88 118 formed between the two ring collars 94, 96 flows.
  • a control edge 120 is formed on the collar 100, via which the connection from port 106 to port 116 is taxable. Covered in the control position of the piston 88 the collar 94 with zero overlap the connection 114.
  • Am Ring collar 94, two control edges 122 and 124 are formed, port 114 via control edge 122 to the port 106 and via the control edge 124 with the connection 116 is connectable.
  • the connection between the control port 114 and the spring chamber 102 is always blocked off by the collar 96.
  • the control valve 62 shown in FIG. 5 makes it practical the orifice plate 14 and the pressure compensator 16 according to FIG. 1 in one single, simply constructed component summarized.
  • control valve 62 is in the installed position with its left end face in FIG. 5 on the contact shoulder 70 of the pressure channel 64.
  • the control valve 62 is in the depressurized state in the basic position shown in Fig. 5. That is, the return port 116 is through the two ring collars 92, 94 shut off while the control port 114 for connection 106 is open.
  • Pressurized pressure medium is created along the orifice hole 104 a pressure drop, so that on the end faces of the piston 88 sets a pressure difference ⁇ p.
  • a partial flow of the pressure medium flowing through the piston 88 can flow into the control connection 114 via the casing bore 118 and thus via the control channel 76, the groove 80 and the Connection channel 82 in the pressure field delimited by the seal 54 be performed.
  • the pressure plate 42 is then practically through the pressure upstream of the piston 88 against the end faces the wheels 34, 36 pressed.
  • the piston 88 With increasing volume flow, the piston 88 is due to the Pressure difference ⁇ p between the end faces against the force of the Compression spring 100 moved. After a predetermined axial displacement, which corresponds to a limit volume flow, the Piston 88 a control position from which by slight Shifts in one direction or the other the pressure in the back pressure field is lowered so that the gap between the pressure plate 42 and the end faces of the wheels 34, 36 is increased or increased so that the gap narrows Part of the pressure medium is then in the manner described above internally returned from the high pressure area to the low pressure area 38, so that the volumetric efficiency of the pump is reduced becomes.
  • control connection 114 wide open to port 116 and through the control edge 120 the port 106 is opened to the return port 116, so that the area upstream of the orifice bore 104 is connected directly to the return duct 72.
  • This return channel 72 can end in the low pressure region 38 or else with be connected to the tank T. In the former case, that will be Pressure medium returned internally, so that less pressure medium must be removed from the tank T.
  • FIG. 6 shows a simplified comparison with the representation in FIG. 5 illustrated, further embodiment of an inventive Control valve 62.
  • This control valve 62 has essentially the same structure as the embodiment shown in Fig. 5, so that only the differences are discussed below becomes.
  • the piston 88 is shown in the control position, in the control port 114 through the control edges 122 and 124 is controlled (zero coverage). With a further axial displacement of the piston 88 to the right becomes the control port first 114 via the control edge 124 and finally the connection 106 controlled via the control edge 120 to the return connection 116.
  • the above-described embodiment corresponds to that from Fig. 5.
  • control connection 114 via the control edge 122 with the Output port 108, and not as shown in FIG Embodiment connected to the input terminal 106 becomes. This becomes in the embodiment shown in Fig. 6 thereby causing the jacket bore 18 not is formed and a hydraulic via the control edge 122 Connection between the spring chamber 102 and the control connection 114 can be produced.
  • the piston 88 of the shown in Fig. 6 embodiment with a radially recessed End section 98 are carried out with the Damping bore 90 cooperates.
  • precautions should be taken be taken be taken to the pressure medium unhindered by the orifice bore 104 to lead to the output port 108.
  • the return port 116 connected to the tank T.
  • the control connection 114 covers zero so that the print in the back Pressure field is just the right height.
  • the connector 106 will go over the control edge 120 connected to the return port 116 and the pressure medium returned directly to the tank T.
  • a major advantage of the invention is that the control valve 62 in that area of the housing 30 is that due to the eccentricity of the receiving space 32 with a greater wall thickness than that in Fig. 2nd area of the housing wall at the top.
  • Through the tangential Arrangement of the pressure channel 64 can be done in a simple manner be drilled from the outside, so that the manufacturing technology Effort is minimal.
  • control valve 62 can in principle be used in a Use a variety of displacement machine types, for example for vane pumps, gear pumps and the corresponding engine types.
  • a hydraulic displacement machine in which the sealing on the face of rotating displacers via a pressure plate he follows.
  • This pressure plate is connected to a control valve Pressurized, through which the size of the sealing gap can be influenced is.
  • the control valve has one Measuring orifice forming hollow piston, via which a return connection, one connection leading to the consumer and one hydraulic control connection connected to the pressure plate can be controlled are.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
EP00108204A 1999-04-19 2000-04-14 Machine hydraulique volumétrique Withdrawn EP1046819A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19917593A DE19917593C2 (de) 1999-04-19 1999-04-19 Hydraulische Verdrängermaschine
DE19917593 1999-04-19

Publications (2)

Publication Number Publication Date
EP1046819A2 true EP1046819A2 (fr) 2000-10-25
EP1046819A3 EP1046819A3 (fr) 2002-06-05

Family

ID=7905052

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00108204A Withdrawn EP1046819A3 (fr) 1999-04-19 2000-04-14 Machine hydraulique volumétrique

Country Status (3)

Country Link
US (1) US6293777B1 (fr)
EP (1) EP1046819A3 (fr)
DE (1) DE19917593C2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1048879B1 (fr) * 1999-04-30 2004-06-23 Hydraulik-Ring GmbH Alimentation en fluide sous pression d' une transmission de type CVT

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10051492A1 (de) * 2000-10-17 2002-04-18 Aws Appbau Arnold Gmbh Coaxialventil als Mengenregelventil
DE102010064130A1 (de) * 2010-12-23 2012-06-28 Robert Bosch Gmbh Axialscheibe und Zahnradpumpe mit Axialscheibe

Citations (2)

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Publication number Priority date Publication date Assignee Title
US4014630A (en) 1974-06-03 1977-03-29 Trw Inc. Power steering pump
EP0445529B1 (fr) 1990-03-07 1994-10-19 Robert Bosch Gmbh Dispositif hydraulique

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US3822965A (en) * 1972-11-02 1974-07-09 Trw Inc Pumps with servo-type actuation for cheek plate unloading
US4187871A (en) * 1978-02-13 1980-02-12 The United States Of America As Represented By The Secretary Of The Navy Pressure-biased shuttle valve
DE3018649A1 (de) * 1980-05-16 1981-11-26 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Hochdruckpumpe
DE3137001A1 (de) * 1981-09-17 1983-03-24 Walter 6370 Oberursel Schopf Pumpenkombination mit mengenreguliereinrichtung
JPS5893977A (ja) * 1981-11-30 1983-06-03 Kayaba Ind Co Ltd 二段内接ギヤポンプ
US4622992A (en) * 1983-01-17 1986-11-18 Sutherland Ivan E Reaction control valve
JPS60153490A (ja) * 1984-01-20 1985-08-12 Matsushita Electric Ind Co Ltd 能力制御装置付回転式圧縮機
DE3739298C2 (de) * 1987-11-20 1994-01-05 Bosch Gmbh Robert Hydraulische Bremseinrichtung
DE3919939C2 (de) * 1989-06-19 1998-07-30 Bosch Gmbh Robert Hydrostatischer Antrieb
GB8923775D0 (en) * 1989-10-21 1989-12-06 Dowty Hydraulic Units Ltd An hydraulic pump
JP2820556B2 (ja) * 1991-06-21 1998-11-05 日立粉末冶金株式会社 油圧装置
DE4136150A1 (de) * 1991-11-02 1993-05-06 Zf Friedrichshafen Ag, 7990 Friedrichshafen, De Fluegelzellenpumpe
EP0563661A1 (fr) * 1992-03-19 1993-10-06 J.M. Voith GmbH Pompe à engrenages internes avec des éléments d'étanchéité mobiles radialement pour la compensation radiale
DE4322240C2 (de) * 1993-07-03 1997-01-09 Eckerle Rexroth Gmbh Co Kg Hydraulische Innenzahnradmaschine (Pumpe oder Motor)
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Patent Citations (2)

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Publication number Priority date Publication date Assignee Title
US4014630A (en) 1974-06-03 1977-03-29 Trw Inc. Power steering pump
EP0445529B1 (fr) 1990-03-07 1994-10-19 Robert Bosch Gmbh Dispositif hydraulique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1048879B1 (fr) * 1999-04-30 2004-06-23 Hydraulik-Ring GmbH Alimentation en fluide sous pression d' une transmission de type CVT

Also Published As

Publication number Publication date
DE19917593A1 (de) 2000-11-02
US6293777B1 (en) 2001-09-25
DE19917593C2 (de) 2002-05-02
EP1046819A3 (fr) 2002-06-05

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