EP1577556A2 - Pompe à palettes - Google Patents

Pompe à palettes Download PDF

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Publication number
EP1577556A2
EP1577556A2 EP05005552A EP05005552A EP1577556A2 EP 1577556 A2 EP1577556 A2 EP 1577556A2 EP 05005552 A EP05005552 A EP 05005552A EP 05005552 A EP05005552 A EP 05005552A EP 1577556 A2 EP1577556 A2 EP 1577556A2
Authority
EP
European Patent Office
Prior art keywords
pressure
chamber
vane pump
suction
delivery
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Withdrawn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
EP05005552A
Other languages
German (de)
English (en)
Other versions
EP1577556A3 (fr
Inventor
Dieter Dr. Ammon
Thomas Schirle
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.)
Daimler AG
Original Assignee
DaimlerChrysler AG
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 DaimlerChrysler AG filed Critical DaimlerChrysler AG
Publication of EP1577556A2 publication Critical patent/EP1577556A2/fr
Publication of EP1577556A3 publication Critical patent/EP1577556A3/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Withdrawn legal-status Critical Current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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses

Definitions

  • the invention relates to a vane pump after the Preamble of claim 1.
  • the patent DE 196 26 211 C2 describes a Vane pump whose contour ring is designed in such a way that the hydraulic fluid due to a reduction in volume the delivery chamber is precompressible. A pressure jump between Delivery chamber and pressure side of the pump is thus at least for an operating point can be eliminated.
  • the object of the invention is in contrast, a vane pump with precompression in the delivery chamber provide over a wide working range of the pump the noise behavior improved.
  • the vane pump according to the invention has a device on, in a delivery chamber and in a pressure chamber a set the same high pressure.
  • a device on, in a delivery chamber and in a pressure chamber a set the same high pressure.
  • the device lowers the pressure in the pre-compression chamber to the level of pressure in the pressure chamber.
  • no pressure oscillations creating a Noise is avoided.
  • the device avoids the noise even at changing pressures in the pressure range, that of a working pressure a system to be supplied are determined.
  • the invention corresponds to the achievable Precompression pressure to a maximum working pressure of one too supplying system.
  • the delivery chamber designed so that the pressure achievable by precompression is the maximum is in Advantageously, over the entire working area of the supplying system equality of pressure in the conveyor and Pressure chamber in conjunction with simultaneously lower Noise development can be guaranteed.
  • the device comprises a valve that regulates the pressure in the delivery chamber through a Lower connection with the suction area. Is the pressure in the Delivery chamber above the pressure in the pressure chamber, so that regulates Valve hydraulic fluid in the suction from.
  • the valve points a slider and a spring on.
  • the pressure relief valve must have a high dynamic, therefore, is a slider of Pressure relief valve preferably in aluminum. Since the volume flows through the valve are very low is the Slide accordingly small dimensions.
  • the device comprises the delivery chamber delimiting wings, which are acted upon by an underfloor pressure. If the precompressed pressure of the delivery chamber is above the pressure of the pressure chamber, the hydraulic fluid flows from the delivery chamber into the intake and / or pressure chamber between a contour ring and a wing. For this purpose, an underfloor pressure, which determines the contact pressure of the wings on the contour ring, to be adjusted so that the pressure in the delivery chamber is lowered to the level in the pressure chamber.
  • the wing lifts off from the contoured ring and a reduction of Delivery chamber pressure is made possible by an overflow of the hydraulic fluid from the delivery into the suction chamber.
  • the pressure in the delivery chamber is reduced by overflowing the hydraulic fluid from the delivery chamber into the pressure chamber.
  • a device according to the invention can be represented inexpensively by this embodiment.
  • the device a rotatable relative to the suction and pressure pocket Contour ring on, causing the pressure in the delivery chamber to a the same high pressure as in the pressure range is adjustable.
  • About the rotation of the contour ring relative to the intake and Pressure pocket is the amount of precompression of the hydraulic fluid determinable in the delivery chamber.
  • the wings of the Vane pump sweep the inner radius of the Contour ring.
  • a delivery chamber transports that Hydraulic fluid from the intake to the pressure pocket, the Delivery chamber in the range of a structurally determinable Angle of rotation separated from both the suction and the pressure pocket is.
  • the twisted Contour ring such that in the delivery chamber an equal high pressure as in the pressure chamber sets. Thereby are at the coupling of the delivery into the pressure chamber effectively Pressure fluctuations avoided.
  • the contour ring is over a piston-cylinder unit rotatable.
  • a piston-cylinder unit Twists the contour ring opposite the intake and Pressure pocket.
  • the piston-cylinder unit is supported on Contour ring and on the housing of the suction and pressure bag from. By pressurizing the piston-cylinder unit is a fast rotation of the contour ring realized.
  • the twisted Contour ring due to the pressure differences in the suction and the Pressure chamber.
  • the contour ring is rotatably mounted. In the suction and Pressure range are each set to different pressures one.
  • the pressures in the suction and pressure area as well as the pressures in the delivery chamber act on the areas bounding these areas Surfaces of the contour ring.
  • a spring provided that the contour ring in a defined position positioned.
  • the spring is for example as a coil spring, Leaf spring, disc spring or as air spring executable.
  • the Spring is supported on the contour ring and on the housing of the intake and Pressure pocket, the spring force is one of the contour ring twisting force, such as a force of the piston-cylinder unit, opposed.
  • the twist angle of the contour ring can be influenced.
  • the piston-cylinder unit connected to a control device.
  • the Regulating device has a arranged in a housing Slider and a spring on.
  • the control device controls this Piston-cylinder unit such that in the Delivery chamber the same pressure level as in the pressure chamber established.
  • the control device derives from the pressure in the Pressure pocket from the pressure for the piston-cylinder unit. there is the amount of pressure depending on the difference of Regulated pressure in the delivery and the pressure chamber.
  • the Slider regulated hydraulic fluid is to avoid Hydraulic losses and cavitation again the intake pocket controlled closed.
  • the Vane pump two suction, delivery and pressure chambers on.
  • this arrangement is a compact Vane pump with high flow can be displayed.
  • Vane pumps are used in a variety of applications such as steering systems, brake systems, active suspension systems or transmissions due to the compact and cost-effective design.
  • Fig. 1 the structure of a two-stroke vane pump 1 is shown by way of example.
  • a rotor 2 with radially displaceable blades 3 is arranged within a contoured ring 4.
  • the vane pump 1 has two intake regions 5 and two pressure regions 6, each comprising suction and pressure channels, suction and pressure pockets 11, 12 and suction, pressure chambers 7, 8, not shown.
  • a shaft rotates the rotor 2 with the blades 3 in the direction of rotation 10.
  • the function of the vane pump 1 is described below with reference to a lifting side.
  • the vane pump 1 sucks hydraulic fluid.
  • a delivery chamber 8 conveys the sucked-in hydraulic fluid volume in the direction of the pressure region 6, the delivery chamber 8 then communicates with neither the suction nor the duck region 5, 6.
  • the hydraulic fluid volume is coupled into the pressure region 6.
  • the volume decreases, whereby the hydraulic fluid via the pressure pocket 12 is conveyed into a pressure channel.
  • FIG. 2 shows a vane pump 1 which has a first embodiment of a device 13 according to the invention.
  • the circumference of the contour ring 4, the wings 3 and the suction and pressure pocket 11,12 are shown in the diagram in a settlement, hereby is about a twist angle ⁇ the volume of the chambers 7,8,9 representable.
  • the arranged in the real part in the side panels 11,12 pockets are arranged as well as in the following figures in a schematic representation of the chambers 7,8,9.
  • the changes in radius of the contour ring 4 are shown exaggerated for better understanding.
  • the chamber 7 and the upstream chamber 10 in the direction of rotation increase the volume, whereby hydraulic fluid flows into the chambers.
  • the suction process is complete as soon as the volume of the chamber 7 is no longer in connection with the suction pocket 11 when the rotor 2 continues to rotate.
  • the hydraulic fluid undergoes precompression, which is to be matched to the maximum working pressure of the system to be supplied.
  • the contoured ring 4 is designed such that the volume in the delivery chamber 8 is reduced. This embodiment makes it possible that during the coupling of the delivery chamber 8 in the pressure region 6 no pressure pulsation occurs. If the vane pump 1 supplies a system with fluctuating working pressure, a device 13 lowers the pressure in the delivery chamber 8 to the level of the pressure chamber 9.
  • the device 13 in the form of a pressure relief valve comprises a piston 14 arranged in a housing 16 and a spring 15.
  • a first end face 25 of the piston 14 is acted upon by the pressure of the delivery chamber 8, on a second end face 26 the pressure of the pressure chamber 9 and the Force of the spring 15. Due to the pressure in the delivery chamber 8 acts on the piston, a first force component, due to the pressure in the pressure chamber 9 results in a second force component. If the first force component is greater than the second force component plus spring force, the piston 14 shifts to the right in the direction of spring 15. Thus, the delivery chamber 8 is connected to the suction pocket 11, whereby the pressure in the delivery chamber degrades until the second force component and the spring force is greater than the first force component and the piston 14 shifts to the left again.
  • the task of the spring 15 is to hold the piston in a defined position.
  • the spring force is very low, therefore, the pressures in the chambers 8,9 take almost equal values.
  • the device 13 according to the invention if necessary, reduces the pressure in the chamber 8 to the pressure level present in the chamber 9. Noise caused by pressure pulsations can be effectively avoided even with fluctuating pressures in the pressure pocket 12 or in the pressure channel 6.
  • the pressure bag 12 is only one Line without interposition of the device 13 with the Conveying pocket 8 connected. This also eliminates the connection between the device 13 and the suction pocket 11.
  • the pressure in the pressure pocket 12 higher than in the Delivery chamber 8 so hydraulic fluid from the pressure pocket 12th overflow via the line in the delivery chamber 8 and thus the pressure difference and the associated vibrations to reduce.
  • the length and cross section of the pipe and the over the location of the control edges 18 certain overcurrent volume are to optimize for an efficient vibration reduction.
  • Fig. 3 is a second embodiment of a inventive device 13 shown, the same high pressure in the Vorkompressionshunt 8 and in the Pressure chamber 9 sets.
  • the device 13 comprises a piston-cylinder unit 20, a spring 21, a control device 22nd and a rotatable contour ring 4.
  • the piston-cylinder unit 20 is connected to the contour ring 4.
  • By Pressurization of the piston-cylinder unit 20 is the Contour ring 4 with respect to the suction and pressure pocket 11, 12th rotatable.
  • By twisting in or against the Arrow direction 27 is the amount of precompression of the Hydraulic fluid adjustable. For example, the Precompression to when the contour ring 4 in Figure 3 moved against the arrow 27.
  • a spring 21 ensures a defined position positioning of the contour ring 4 and provides a restoring force.
  • the spring 21 is between the Housing of the suction and pressure pockets 11,12 can be arranged, Alternatively, this can also be in the piston-cylinder unit 20th be arranged. To compensate for temperature fluctuations, can the spring 21 is also temperature-sensitive, i. as a bimetallic spring or be designed as a spring with shape memory. Likewise, different springs are in a parallel or Connected in series with each other.
  • a Regulating device 22 determines the operating pressure for the Piston-cylinder unit 20.
  • the control device 22 has a Slider 23 and a spring 24 in a housing 25th are arranged on. As pilot pressure is the slide 23rd on a first end face 25 of the pressure from the Pressure pocket 12 connected, a second end face 26 is the pressure of the delivery chamber 8 and the force of the spring 24th switched.
  • the following is the operation of the invention Device 13 described.
  • the spring 24 pushes the slide 23 in a position in which the line connected to the piston-cylinder unit with the suction area 11 is, so that the spring 21 the contour ring 4 in the direction of arrow 27th can twist.
  • the contour ring 4 is designed so that in this position, the volume of the delivery chamber 8 does not change.
  • the device 13 comprises a spring 21 and a contoured ring 4 rotatable by an angle ⁇ .
  • the contoured ring 4 is supported on the spring 21, which is connected to the housing of the suction and pressure pockets 11,12.
  • the contoured ring 4 is thus against the force of the spring 21 relative to the suction and pressure pocket 11,12 rotatable.
  • no piston-cylinder unit 20 is provided in contrast to the embodiment in Fig. 3.
  • the force rotating the contour ring 4 results directly from the pressures in the intake, delivery and pressure chambers 7,8,9.
  • the areas A7 to A9 are each calculated from the effective Chamber height multiplied by a not shown Chamber depth. Is the working pressure of a system to be supplied low, the spring 21 pushes the contour ring 4 in one Position that no precompression in the delivery chamber. 8 allows. In this position the area A8 has the value zero, the areas A7 and A9 are the same size. The difference of the pressures p7 and P9 resulting force Fk is of the Spring 21 supported.
  • the contoured ring 4 rotates by an angle ⁇ .
  • the contour ring is denoted by 4 '.
  • the rotation causes the delivery chamber 8 to be enlarged by a volume 8 '.
  • the hydraulic fluid undergoes precompression because the volume of the delivery chamber 8 is reduced by the volume 8 'until it is coupled into the pressure pocket 12.
  • Due to a low compressibility of the hydraulic fluid, for example oil at 3 * 10 -5 / bar the required compression volume 8 'is small. With a loss-free calculation for a coupling pressure of 135 bar, this is less than 1% of the volume of the delivery chamber 8.
  • the system is tunable so that the pressure in the Delivery chamber 8 in the coupling exactly the system working pressure corresponds and disturbing noises in connection with Pressure pulsations even at changing system operating pressures, i.e. fluctuating pressures in the pressure range 6, are avoidable.
  • the vote is essentially about the design of the Contour ring 4 and the spring 21.
  • To represent a suitable spring characteristic are also several springs in parallel and / or switchable in a row.
  • a modified, not shown embodiment is to adjust the Vorkompressions réellees in the Delivery chamber 8, the suction bag 11 and / or the pressure pocket 12th rotatable relative to the contour ring. For example, twist the side panels over a suitable device such that in the delivery chamber and the pressure chamber an equal high pressure setting.
  • a shift of the in Fig. 1,2 shown control edges 18 allows.
  • the amount of precompression is adjustable, so that in the coupling of the delivery chamber 8 in the Pressure chamber 9 no pressure surges occur.
  • FIG. 5 shows a vane pump in which the device 13 comprises a vane 3 and a throttle device for controlling the underwing pressure.
  • a wing 3 is indicated in position 3 '.
  • the adjustment of the pressure in the delivery chamber 8 to the level of the pressure in the pressure chamber is made possible by an overflow of the hydraulic fluid between the wing 3 'and the contour ring 4.
  • the wings 3 are acted upon by an underfloor pressure equal to the pressure in the pressure chamber 9.
  • the pressure from arranged in a side plate pressure pocket 12 is guided via a channel, not shown, in the side plate in the lower wing region 36.
  • the pressure is applied between the rotating rotor 2 and a stationary stator ring 33 connected to the contour ring 4 and the side plate.
  • the wing designated by the reference numeral 3 ' defines the suction and delivery chamber 7,8 from each other. Due to the shape of the blade, the pressure in the suction chamber 7 and on the other half the pressure of the delivery chamber 8 acts on the face of the blade 3 in contact with the contoured ring 4. Since the suction pressure has a small value, is the resulting force component on the wing 3 'negligible. Via a throttle device with the throttles 28,29,30 the lower wing side of the wing 3 'is delivered a pressure which is half as large as the pressure in the pressure chamber 9. Thus lifts the wing 3' from the contour ring 4, as soon as the precompressed pressure in the delivery chamber 8 exceeds the pressure in the pressure chamber 9. The hydraulic fluid flowing out via the throttle 3 flows back into the intake pocket 11 via a return line 31. Hydraulic fluid flows as long as the delivery into the suction 8.7 to equal pressure in the delivery and pressure chamber is reached 7.9.
  • the throttle device is constructed so that of Untererieldruck the wing 3 a hydraulic flow branches off and on the first and second throttle 28,29 in the Untereriel Scheme of the wing 3 'flows. From this area the hydraulic volume flow flows in via the third throttle 30 a pipe connected to the suction pocket 11. are the flow resistances of the throttles 28,29 twice as large as the flow resistance of the throttle 30, so arises in the Under wing area of the wing 3 'a pressure a half way is great as the pressure in the pressure chamber. 9
  • Throttles 28,29,30 are of course others Under wing pressures adjustable. For example, this is one Vorkompressions réelle in the delivery chamber 8 adjustable, the is below or above the pressure level in the pressure chamber 9. There are also pressure drops due to leaks occur by changing the underfloor pressure on the wing 3 ' compensated.
  • a device is shown, which is based on a Throttle device omitted.
  • the with the contour ring 4 in Touching face is designed so that For example, on the front side of the wing 3 'of the pressure of Delivery chamber 8 acts. In the entire under wing area 36 is the pressure of the pressure chamber 9 at. This lifts the wing 3 ' from the contour ring 4, as soon as the precompressed pressure in the Delivery chamber 8 exceeds the pressure in the pressure chamber 9, which an adjustment of the pressure in the delivery chamber 8 to the level the pressure in the pressure chamber 9 takes place.
  • the wings of the variant shown in Fig. 7 are such designed to be in contact with the contour ring 4 standing front side of the wing 3 '' one in the in the Delivery chamber 8 pending pressure resulting force acts.
  • the reference numeral 3 '' designated wing 3 borders the Delivery and pressure chamber 8.9 from each other.
  • the Untereriel Scheme 36 is with the pressure from the pressure chamber. 9 applied. If the pressure in the delivery chamber 8 rises above the Pressure in the pressure chamber 9, so lifts the wing 3 "of the Contour ring 4 off, leaving itself in the delivery and pressure chamber can again set a pressure of the same height.
  • FIG. 8 shows an arrangement for reinforcing the Wing contact pressure shown.
  • the area 35, at the Pressure of the pressure chamber 9 is present, is about the arrangement of a Reinforcing piston 34 increases. This increases the power with the wings 3 are pressed against the contour ring 4.
  • the room on the opposite side of the Reinforcing piston is connected to the suction pocket 11, so that there is no counterforce on this side.
  • the Arrangement can be used, for example, if due to Leaks in the delivery chamber 8 and / or pressure chamber 9 not a build up enough pressure.
  • the above-described devices 13 for adjusting a Pressure of the same height in the delivery and pressure chamber are 8.9 of course also combinable with each other. All Devices are in single-barreled and / or regulated Vane pumps 1 can be used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP05005552A 2004-03-18 2005-03-15 Pompe à palettes Withdrawn EP1577556A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004013230A DE102004013230A1 (de) 2004-03-18 2004-03-18 Flügelzellenpumpe
DE102004013230 2004-03-18

Publications (2)

Publication Number Publication Date
EP1577556A2 true EP1577556A2 (fr) 2005-09-21
EP1577556A3 EP1577556A3 (fr) 2005-11-30

Family

ID=34833165

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05005552A Withdrawn EP1577556A3 (fr) 2004-03-18 2005-03-15 Pompe à palettes

Country Status (3)

Country Link
US (1) US20050207916A1 (fr)
EP (1) EP1577556A3 (fr)
DE (1) DE102004013230A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008046005A2 (fr) * 2006-10-11 2008-04-17 Parker-Hannifin Corporation Passage limiteur de pre-compression pour pompes volumetriques
DE102007060883A1 (de) 2007-12-18 2009-06-25 Robert Bosch Gmbh Hydraulische Arbeitsmaschine

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBO20030528A1 (it) * 2003-09-12 2005-03-13 Pierburg Spa Impianto di pompaggio utilizzante una pompa a palette
DE102006033337A1 (de) * 2006-07-19 2008-01-24 Zf Lenksysteme Gmbh Verdrängerpumpe
DE102009000155A1 (de) * 2009-01-13 2010-07-15 Zf Lenksysteme Gmbh Flügelzellenpumpe
JP2014015906A (ja) * 2012-07-10 2014-01-30 Hitachi Automotive Systems Ltd ポンプ装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05133351A (ja) * 1991-11-11 1993-05-28 Jidosha Kiki Co Ltd ベーンポンプ
DE4224592A1 (de) * 1992-07-22 1994-01-27 Volvo Hydraulik Engineering Gm Hydraulische Verdrängerpumpe
EP0718497A1 (fr) * 1994-12-19 1996-06-26 Albert Handtmann Maschinenfabrik GmbH & Co. KG Pompe à palettes

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5996492A (ja) * 1982-11-22 1984-06-02 Jidosha Kiki Co Ltd オイルポンプ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05133351A (ja) * 1991-11-11 1993-05-28 Jidosha Kiki Co Ltd ベーンポンプ
DE4224592A1 (de) * 1992-07-22 1994-01-27 Volvo Hydraulik Engineering Gm Hydraulische Verdrängerpumpe
EP0718497A1 (fr) * 1994-12-19 1996-06-26 Albert Handtmann Maschinenfabrik GmbH & Co. KG Pompe à palettes

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN Bd. 017, Nr. 517 (M-1481), 17. September 1993 (1993-09-17) -& JP 05 133351 A (JIDOSHA KIKI CO LTD), 28. Mai 1993 (1993-05-28) *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008046005A2 (fr) * 2006-10-11 2008-04-17 Parker-Hannifin Corporation Passage limiteur de pre-compression pour pompes volumetriques
WO2008046005A3 (fr) * 2006-10-11 2008-05-29 Parker Hannifin Corp Passage limiteur de pre-compression pour pompes volumetriques
DE102007060883A1 (de) 2007-12-18 2009-06-25 Robert Bosch Gmbh Hydraulische Arbeitsmaschine

Also Published As

Publication number Publication date
EP1577556A3 (fr) 2005-11-30
US20050207916A1 (en) 2005-09-22
DE102004013230A1 (de) 2005-10-06

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