EP0254077A2 - Pompe à engrenages internes - Google Patents

Pompe à engrenages internes Download PDF

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Publication number
EP0254077A2
EP0254077A2 EP87109295A EP87109295A EP0254077A2 EP 0254077 A2 EP0254077 A2 EP 0254077A2 EP 87109295 A EP87109295 A EP 87109295A EP 87109295 A EP87109295 A EP 87109295A EP 0254077 A2 EP0254077 A2 EP 0254077A2
Authority
EP
European Patent Office
Prior art keywords
flanks
ring gear
tooth
teeth
coverage
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.)
Granted
Application number
EP87109295A
Other languages
German (de)
English (en)
Other versions
EP0254077A3 (en
EP0254077B1 (fr
Inventor
Siegfried Hertell
Dieter Otto
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.)
Oerlikon Barmag AG
Original Assignee
Barmag AG
Barmag Barmer Maschinenfabrik 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
Priority claimed from DE19863624517 external-priority patent/DE3624517A1/de
Application filed by Barmag AG, Barmag Barmer Maschinenfabrik AG filed Critical Barmag AG
Publication of EP0254077A2 publication Critical patent/EP0254077A2/fr
Publication of EP0254077A3 publication Critical patent/EP0254077A3/de
Application granted granted Critical
Publication of EP0254077B1 publication Critical patent/EP0254077B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps
    • F04C15/066—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type
    • F04C15/068—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type of the elastic type, e.g. reed 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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

Definitions

  • the invention relates to an internal gear pump with a driving pinion and a ring gear, in which on the pressure side the trailing flanks of the teeth of the pinion (sealing flanks of the pinion) with the corresponding counter flanks of the ring gear (sealing flanks of the ring gear) in the area between the intersection of the tip circles and the Rolling point with a degree of coverage greater than 2 are engaged.
  • Internal gear pumps of this type serve as control pumps for hydraulic fluids.
  • they are provided with a large number of outlet openings, the pitch of which is smaller than or equal to the tooth pitch.
  • These outlet openings all or in groups lead to a common pressure channel and - with one exception if any - all outlet openings of a group are closed by a check valve.
  • the internal gear pump has a delivery characteristic that is speed-dependent only up to a certain speed.
  • the delivery is constant above this speed.
  • the threshold speed can be adjusted by adjusting a throttle in the inlet.
  • Such an internal gear pump is known from DE-OS 34 44 859.
  • This internal gear pump has the peculiarity compared to conventional internal gear pumps that there is a degree of coverage of at least 2, so that the internal gear pump has at least two, but preferably three or more, mutually sealed toothed cells on the suction and printing page forms.
  • control pumps of this type are used with particular advantage for driving motor vehicle engines, the speed of which fluctuates greatly. There they serve as hydraulic pumps or lubricating oil pumps, since with these pumps the maximum delivery rate can be limited without loss of performance at a certain, relatively low speed.
  • the invention has for its object to further reduce the power requirement of the known internal gear pump.
  • the tooth flanks For this purpose, it is proposed to design the tooth flanks so that the driving flanks have less coverage than the sealing flanks.
  • the profile coverage of a toothing represents the ratio of the engagement length to the pitch. In a gear pump, the profile coverage is, among other factors, also decisive for the sealing effect of the sealing tooth flanks.
  • This solution is particularly advantageous in the low pressure range - up to approx. 20 bar - and in particular in the automotive sector, where it is important to achieve a maximum delivery rate at relatively low speeds, while keeping the idle power and in particular the mechanical power consumption of the pump low.
  • a preferred field of application are lubricating oil pumps which are arranged in the sump of the motor vehicle engine.
  • the proposed solution includes that the tooth flanks of the pinion and / or the tooth flanks of the ring gear on the driving side and the sealing side are not made mirror-symmetrical. It is essential that the tooth flanks of the driving side have only a relatively small area in which the driving flanks of the pinion and ring gear can come into engagement with one another (engagement area). This meshing area lies - for pinion and ring gear alike - between the pitch circle and the tip circle and begins at the pitch circle.
  • the tooth flanks created by conventional toothing processes can be removed or deformed in such a way that no tooth engagement occurs.
  • the asymmetrical tooth shape proposed here can advantageously also be produced in a sintering process, since a corresponding shaping is possible here without subsequent mechanical processing.
  • the engagement area is preferably chosen to be so large that the degree of coverage is between 1 and 2. On the one hand, this relatively low degree of coverage results in a considerable reduction in the mechanical power consumption. On the other hand, with this degree of coverage, in particular in the case of hydraulic pumps in the low-pressure range, there is no unacceptable wear.
  • the reduction of the flow velocities and the power consumption caused thereby serves alone or in combination with the other measures of this invention that the outlet openings between the line of engagement and the outer circumference of the ring gear, preferably between the line of engagement and the root circle of the ring gear, are created, with only one towards the line of engagement narrow sealing web is retained.
  • the cross section of the openings is essentially adapted to the cross section of the teeth of the ring gear minus a narrow sealing strip. The cross section of a tooth thus completely covers the outlet opening, but the area of the outlet opening comes as close as possible to the area of the tooth cross section.
  • the outer wheel 1 is freely rotatably mounted in the housing 31.
  • the outer wheel 1 has an internal toothing 2.
  • the cylindrical housing 31 is closed on both sides by the covers 32 and 33.
  • the shaft 34 is rotatably supported and driven by the motor vehicle engine, not shown.
  • the inner wheel 3 is rotatably mounted on the shaft 34.
  • the inner wheel 3 has an external toothing 4 which is in engagement with the internal toothing 2 of the outer wheel 1.
  • the interior of the pump which lies outside the meshing of the teeth, can be filled with a sickle that largely conforms to the tip circles of the gears.
  • In the cover 33 there is the inlet channel 35 (see also FIG. 2).
  • the inlet channel 35 is connected to the sump 36 via a throttle 37.
  • a pressure control valve 39 is located in a bypass 38, which is connected in parallel to the throttle channel 37.
  • the piston 40 of the pressure control valve controls the opening of the bypass channel 38 to the sump 36 with its control edge 41.
  • the piston is on one side with a spring 42 charged.
  • the piston in control chamber 43 is acted upon by the outlet pressure in pressure channel 56 via control line 44.
  • the outlet side of the pump will be discussed later.
  • the function of the pressure control valve 39 as a function of the outlet pressure is described below. As long as there is no or only a low outlet pressure in the control line 44 and the control chamber 43, the piston with its control edge releases the flow from the inlet 45 to the outlet 46.
  • the pump forms - as shown in FIG. 1 - on the outlet side between the meshing teeth of the outer wheel 1 and inner wheel 3 three cells which are closed in the circumferential direction and in the axial direction and which have been completely or partially filled with oil via inlet channel 35.
  • cover 33 three outlet openings 48.1, 48.3, 48.5 are introduced.
  • Two outlet openings 48.2, 48.4 are introduced into the cover 32.
  • the outlet openings of the cover 33 are arranged offset with respect to the outlet openings of the cover 32. When projected onto a normal plane, the outlet openings in the cover 33 or 32 do not overlap - as shown in FIG. 1.
  • the outlet openings nestle closely with their radially inner edge 27 (inner edge) to the line of engagement 11, in such a way that only a narrow, but sufficiently sealing sealing web 28 remains between the line of engagement 11 and the inner edge 27.
  • the width of the outlet openings 48.1 to 48.5 is selected so that the outlet openings are covered by the cross section of the teeth 2 of the ring gear 1 with the teeth in a corresponding position, sufficient sealing surfaces also remaining in the circumferential direction.
  • the outlet openings extend into the area of the outer circumference of the ring gear and in any case up to the outermost area with which the bottom of the tooth gaps of the ring gear 1 opens on the end face of the covers 32, 33.
  • tooth space base 30 represents half the jacket of a circular cylinder, the axis of which lies on the plane of symmetry of the tooth space and essentially on the pitch circle or slightly radially outside of the pitch circle 7 of the ring gear.
  • the bottom of the tooth space is again provided with a funnel-shaped extension 26 at both ends.
  • the funnel-shaped extension 26 extends radially to almost the outer circumference of the ring gear.
  • the funnel-shaped extension 26 can also extend in the circumferential direction. However, it is in any case radially outside of the pitch circle 7 of the ring gear 1. If the oil outlet is only provided on one side in a pump according to the invention, the funnel-shaped extension is also only on the relevant side.
  • each outlet opening is connected to an outlet channel 49 drilled in the cover 32, 33.
  • the outlet channel is also directed radially outwards, as shown in FIG. 2. Therefore each outlet channel opens 49 on the outside of the cover 32 and 33 as close as possible to the housing 31.
  • An outlet housing 50 is placed pressure-tight on each cover 32, 33.
  • Each outlet housing 50 forms an outlet chamber which is connected on one side to the outlet openings 48.1, 48.3, 48.5 and on the other side to the outlet openings 48.2, 48.4 each via a pressure channel 49 and a bore 52.
  • the bores 52 (cf. FIG. 1) are each closed by a check valve, with the exception of the bore which is connected to the outlet opening 48.5.
  • the outlet opening 48.5 is located at the end of the pressure zone immediately before the pitch point. Both outlet chambers are connected to the common pressure channel 56.
  • the check valves on both sides are formed by an n-shaped plate, which is screwed against the wall 53 of the outlet housing 50.
  • the tongues protruding from the common crossbeam 55 of the check valve 54 cover the bores 52. Therefore, these tongues act as check valves.
  • Each check valve only releases the connection from the respective pressure cell formed between the teeth via one of the outlet openings 48, pressure channels 49 and bores 52 if the pressure of the outlet cell is at least equal to the outlet pressure in the outlet chamber 51.
  • the last and smallest pressure cell is directly connected to the outlet chamber via opening 48.5 and corresponding channels 49, 52.
  • Each outlet chamber 51 has an outlet which leads into the common pressure oil channel 56.
  • both flanks of each tooth are formed according to a special toothing law.
  • This gearing law ensures that there is a high degree of coverage, greater than 2, preferably is greater than 3. This has the effect that the teeth are in engagement with one another in approximately the entire rotational range between the intersection of the two tip circles 5 and 9 and the pitch point and, as a result, more than two tooth cells are formed by two successive tooth pairs in each case. These tooth cells are mutually closed in the circumferential direction.
  • This gearing law includes that the driving flanks of the inner wheel 3 and outer wheel 1 also have a correspondingly large degree of coverage. It is now provided that the degree of coverage is less on the driving side of the teeth than on the sealing side of the teeth.
  • the tooth flanks which lie on top of each other in the pressure zone between the intersection of the tip circles and the pitch point and form the tooth cells that are sealed off from each other, are produced according to the toothing law described above. These flanks are referred to as sealing flanks in the context of this application.
  • flanks of the teeth of ring gear 1 and pinion 3, which serve to transmit the torque between inner wheel 3 and ring gear 1 (driving flanks), are produced with a lower degree of coverage, which is preferably between 1 and 2. This is done in that only a partial area of the driving flanks of the outer wheel 1 and / or the inner wheel 3 is produced according to the toothing law (engagement area of the flank).
  • the engagement area 64 of the drive flanks of the ring gear extends radially a little way inward from the pitch circle 7 of the ring gear.
  • the cross-sectional area by which the driving flank of the ring gear deviates from the profile produced by toothing is designated by 65.
  • the engagement area 66 of the drive flanks of the inner wheel 1 extends radially a little outward from the pitch circle 8.
  • the cross-sectional area of the tooth head by which the driving tooth flanks of the inner wheel 3 recede relative to the ideal tooth profile is designated by 67.
  • either the driving flanks of the ring gear or the driving flanks of the pinion or both can be provided with such cutouts 65 and 67, respectively.
  • the latter solution has the advantage that only low flow velocities arise on the suction side of the pump.
  • the engagement area 64 of the driving flanks of the ring gear and / or the inner wheel which is formed according to the gearing law, is dimensioned such that on the one hand at least one pair of teeth of the ring gear and the inner wheel are always in engagement with one another, but on the other hand fewer tooth pairs are in engagement on the driving side than on the Sealing side.
  • the degree of coverage on the engagement side is preferably not greater than 2 due to the correspondingly short design of the engagement areas.
  • the spring 42 moves the piston 40 - in Fig. 2 - to the left.
  • the pump now acts like a normal internal gear pump.
  • the lubricating oil flow flows through throttle 37 and bypass channel 38 to the inlet. All tooth gaps are filled to the maximum and expressed again on the outlet side. The degree of filling depends on how far the bypass 38 is throttled. This will be discussed later. In any case, full filling takes place at low speeds.
  • This operating state is maintained at low speeds of the motor vehicle engine.
  • the lubricating oil flow is therefore proportional to the demand according to the speed.
  • the bypass 38 is initially closed or at least severely throttled by the pressure control valve 39.
  • the tooth gaps on the inlet side are only partially filled.
  • the pressure in the tooth cells on the outlet side is initially lower than the pressure in the outlet chamber 51. Therefore, the respective tongues of the check valve 54 remain closed.
  • the pressure in the cells increases. Only the tongue of the check valve opens for which the pressure of the cell is greater than or equal to the pressure in the outlet chamber 51. The result of this is that the pump now only delivers a constant, independent oil quantity.
  • the lubricating oil pump also meets other requirements of special operating conditions. For example, occur that the lubricating oil heats up excessively or that engine parts must be cooled by lubricating oil due to special performance requirements.
  • a further short-circuit channel 58 is provided between the inlet 35 of the pump and the oil sump 36.
  • An electromagnetically switched valve 59 is located in this short-circuit channel. This valve is actuated via signal line 60 and amplifier 61 by a temperature sensor 62.
  • the temperature sensor can e.g. the oil temperature or the temperature of a machine part, e.g. Pistons to be detected. It is also possible to use a different measuring instrument, e.g. Speed counter to use.
  • the message line can also be used to record other extraordinary operating conditions.
  • the valve 59 serves the purpose of meeting an extraordinary need. It is assumed here that the sum of the oil flow, which is conveyed by throttle 37 on the one hand and via bypass 38 on the other hand, is still throttled and therefore only partial filling of the cells of the internal toothing takes place even at open pressure control valve at speeds that exceed one certain threshold speed. Fig. 2 meets this requirement in that a further throttle 63 in the bypass 38 is indicated as a symbol.
  • the pressure limiting valve can be operated by valve 68, which is switched electromagnetically, for example by the temperature of a machine part. either the pressure upstream of the throttle 37 or the pressure downstream of the throttle 37.
  • the configuration of the exemplary embodiment shown avoids that unnecessarily high power losses occur as a result of the cell formation and the emptying of the cells.
  • this is achieved in that the degree of coverage on the drive side of the teeth is less than on the sealing side of the teeth.
  • a balance must be made here between avoiding mechanical loss of performance on the one hand and increased wear on the other. This consideration depends on the application of the pump. Power losses play a smaller role in high-pressure hydraulic pumps.
  • the flow rate of the oil to be pressed out of the tooth space can be very greatly reduced, especially in the area shortly before bottom dead center.
  • the expansion of the tooth gap of the ring gear can be driven radially outside of the pitch circle 7 until the stability limit of the ring gear is reached.
  • the maximum flow rate when the oil was pressed out was reduced from 20 m / sec to 5 m / sec. This reduction in flow velocity also means a reduction in hydraulic power losses.
  • outlet openings are arranged radially outside the line of engagement while maintaining a narrow but sufficient sealing strip ensures that there is no short circuit between successive tooth cells via the outlet openings.
  • this enables the outlet openings to be made over a very large area.
  • the area of the outlet openings is selected so that it is covered by the tooth cross section of the ring gear with sufficiently wide sealing surfaces in the circumferential direction.
  • the outlet openings can be chosen to be very large and the outlet openings can furthermore be arranged with a smaller pitch than the tooth pitch. This ensures that there is always a large connection cross-section between the tooth cells and the outlet.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP87109295A 1986-07-19 1987-06-27 Pompe à engrenages internes Expired - Lifetime EP0254077B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3624517 1986-07-19
DE19863624517 DE3624517A1 (de) 1986-07-19 1986-07-19 Innenzahnradpumpe
DE3704548 1987-02-13
DE3704548 1987-02-13

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP89122024.6 Division-Into 1987-06-27

Publications (3)

Publication Number Publication Date
EP0254077A2 true EP0254077A2 (fr) 1988-01-27
EP0254077A3 EP0254077A3 (en) 1988-03-09
EP0254077B1 EP0254077B1 (fr) 1990-11-14

Family

ID=25845735

Family Applications (2)

Application Number Title Priority Date Filing Date
EP87109295A Expired - Lifetime EP0254077B1 (fr) 1986-07-19 1987-06-27 Pompe à engrenages internes
EP89122024A Expired - Lifetime EP0362906B1 (fr) 1986-07-19 1987-06-27 Pompe à engrènement interne

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP89122024A Expired - Lifetime EP0362906B1 (fr) 1986-07-19 1987-06-27 Pompe à engrènement interne

Country Status (4)

Country Link
US (1) US4813853A (fr)
EP (2) EP0254077B1 (fr)
DE (2) DE3772775D1 (fr)
ES (2) ES2022841B3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3737961A1 (de) * 1987-11-07 1989-05-18 Barmag Barmer Maschf Innenzahnradpumpe
DE4107704A1 (de) * 1990-03-15 1991-09-19 Barmag Luk Automobiltech Hydraulikpumpe
WO2013092966A3 (fr) * 2011-12-22 2014-02-13 Robert Bosch Gmbh Pompe à roue dentée intérieure

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US6192925B1 (en) * 1999-10-06 2001-02-27 Der-Fan Shen Flow regulator for water pump
DE10052779A1 (de) * 2000-10-25 2002-05-08 Eckerle Ind Elektronik Gmbh Füllstücklose Innenzahnradpumpe
US20060127264A1 (en) * 2001-02-01 2006-06-15 Giovanni Aquino Multi-vane device
US6853954B2 (en) 2002-09-24 2005-02-08 John K. Apostolides Methods and systems for collecting and processing data in association with machine operation and maintenance
JP4169724B2 (ja) * 2003-07-17 2008-10-22 株式会社山田製作所 トロコイド型オイルポンプ
ES2416312T3 (es) * 2004-06-24 2013-07-31 Ixetic Hückeswagen Gmbh Bomba
JP4319617B2 (ja) * 2004-12-27 2009-08-26 株式会社山田製作所 トロコイド型オイルポンプ
JP4916155B2 (ja) 2004-12-28 2012-04-11 デルタ工業株式会社 リクライニング装置
WO2009091980A1 (fr) * 2008-01-17 2009-07-23 Fisher Dynamics Corporation Mécanisme de siège inclinable rond
JP5795726B2 (ja) * 2011-06-27 2015-10-14 株式会社山田製作所 オイルポンプ
US9296315B2 (en) 2013-02-26 2016-03-29 Fisher & Company, Incorporated Recliner mechanism with backdriving feature
US9902297B2 (en) 2014-06-11 2018-02-27 Fisher & Company, Incorporated Latch mechanism with locking feature
JP6682300B2 (ja) * 2016-03-04 2020-04-15 シロキ工業株式会社 シートリクライニング装置
EP4295046A4 (fr) 2021-02-19 2024-12-18 1158992 B.C. Ltd. Dispositif de transfert de fluide

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US4553966A (en) * 1983-09-19 1985-11-19 Americal Corporation Device for draining body fluids and irrigating solutions
DE3444859A1 (de) * 1983-12-14 1985-06-27 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Rotationszellenpumpe fuer hydrauliksysteme
CH667702A5 (de) * 1984-02-15 1988-10-31 Barmag Barmer Maschf Zahnradpumpe.
DE3506629A1 (de) * 1984-03-01 1985-10-03 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Hydrauliksysteme
DE8406556U1 (de) * 1984-03-02 1985-06-27 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Zahnradpumpe mit plattenförmigem Gehäuse
JPS614882A (ja) * 1984-06-18 1986-01-10 Toyoda Mach Works Ltd 歯車ポンプ
JPS618484A (ja) * 1984-06-22 1986-01-16 Mitsubishi Metal Corp 内接型ギヤポンプ
DE3481536D1 (de) * 1984-09-05 1990-04-12 Hobourn Engineering Ltd Pumpen.
GB2167130B (en) * 1984-11-19 1988-01-13 Hydrovane Compressor Rotary positive displacement air compressor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3737961A1 (de) * 1987-11-07 1989-05-18 Barmag Barmer Maschf Innenzahnradpumpe
DE4107704A1 (de) * 1990-03-15 1991-09-19 Barmag Luk Automobiltech Hydraulikpumpe
WO2013092966A3 (fr) * 2011-12-22 2014-02-13 Robert Bosch Gmbh Pompe à roue dentée intérieure

Also Published As

Publication number Publication date
EP0362906A2 (fr) 1990-04-11
EP0254077A3 (en) 1988-03-09
DE3772775D1 (de) 1991-10-10
EP0362906A3 (en) 1990-05-30
US4813853A (en) 1989-03-21
EP0362906B1 (fr) 1991-09-04
EP0254077B1 (fr) 1990-11-14
ES2022841B3 (es) 1991-12-16
ES2024708B3 (es) 1992-03-01
DE3766177D1 (de) 1990-12-20

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