EP0254077B1 - Pompe à engrenages internes - Google Patents

Pompe à engrenages internes Download PDF

Info

Publication number
EP0254077B1
EP0254077B1 EP87109295A EP87109295A EP0254077B1 EP 0254077 B1 EP0254077 B1 EP 0254077B1 EP 87109295 A EP87109295 A EP 87109295A EP 87109295 A EP87109295 A EP 87109295A EP 0254077 B1 EP0254077 B1 EP 0254077B1
Authority
EP
European Patent Office
Prior art keywords
tooth
flanks
internal
geared wheel
gear pump
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.)
Expired - Lifetime
Application number
EP87109295A
Other languages
German (de)
English (en)
Other versions
EP0254077A3 (en
EP0254077A2 (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
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 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

Links

Images

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 pinion teeth (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 tooth rows which are closed off from one another 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. They are used there 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 profile overlap of a toothing represents the ratio of the engagement length to the pitch.
  • the profile overlap is, among other factors, also decisive for the sealing effect of the sealing tooth flanks.
  • Deviating from the technical term of profile overlap, in the context of this application the overlap indicates the number of tooth pairs on the suction or pressure side that are in engagement with one another on average, i.e. touch or face each other with little backlash that causes the seal.
  • 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 impermissible 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 Cut 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 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.
  • each outlet opening 49 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 49 opens out on the outside of the cover 32 and 33 as close as possible to the housing 31.
  • An outlet housing 50 is placed on each cover 32, 33 in a pressure-tight manner.
  • 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 interlocking law ensures that there is a high degree of coverage that is greater than 2, preferably 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 sealingly on top of each other in the pressure zone between the intersection of the tip circles and the pitch point and form the mutually closed tooth cells, 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.
  • 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.
  • 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. It only opens the tongue of the check valve 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 have to 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 spring side 42 of the pressure control valve 39 by a suitable valve from a low pressure, at which a relatively low outlet pressure is regulated on the outlet side of the pump via line 44, to a low pressure, at which the outlet pressure is increased accordingly.
  • a suitable valve As shown in Fig. 3, e.g. the pressure relief valve through the valve 68 which is electromagnetically e.g. is switched by the temperature of a machine part, either to the pressure before the throttle 37 or to the pressure behind 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (7)

1. Pompe à engrenage intérieur, avec un pignon menant (3) et une roue creuse ou couronne (1), dans laquelle, sur le côté refoulement, les flancs arrière des dents du pignon, qui forment les flancs d'étanchéité du pignon, sont en contact avec les flancs conjugués correspondants des dents de la couronne, qui forment les flancs d'étanchéité de la couronne, dans la zone située entre le point d'intersection des cercles de tête et le point d'action, avec un degré de recouvrement égal ou supérieur à 2, de façon à former une pluralité de cellules dentées isolées les unes des autres, plusieurs de ces cellules étant reliées au canal de refoulement commun par l'intermédiaire d'au moins un échappement comportant un clapet anti-retour, caractérisée en ce que les flancs menants des dents du pignon (3) et les flancs menants conjugués correspondants des dents de la couronne présentent sur le côté aspiration de la pompe un degré de recouvrement inférieur à celui des flancs d'étanchéité sur le côté du refoulement.
2. Pompe à engrenage intérieur selon la revendication 1, caractérisée en ce que le degré de recouvrement des flancs d'étanchéité est égal ou supérieur à 3 et que le degré de recouvrement des flancs menants est compris entre 1 et 2.
3. Pompe à engrenage intérieur selon la revendication 1 ou 2, caractérisée en ce que les entredents de la couronne, dans la mesure où ils se situent à l'extérieur du cercle primitif, sont notablement agrandis en section transversale par rapport à la courbe d'enveloppe d'une dent de pignon.
4. Pompe à engrenage intérieur selon l'une des revendications 1 à 3, caractérisée en ce que déduction faite d'une faible bande d'étanchéité, les ouvertures d'échappement sont légèrement plus petites que la section transversale de dent de la couronne.
5. Pompe à engrenage intérieur selon l'une des revendications précédentes, caractérisée en ce que les ouvertures d'échappement sont situées entre la ligne d'action et le cercle périphérique de la couronne et approchent de la ligne d'action en laissant subsister une étroite surface d'étanchéité.
6. Pompe à engrenage intérieur selon l'une des revendications 3 à 5, caractérisée en ce que le fond des entredents de la couronne, sur le côté frontal tourné vers les ouvertures d'échappement, est agrandi en forme d'entonnoir jusqu'à peu près à la périphérie de la couronne.
7. Pompe à engrenage intérieur selon l'une des revendications précédentes, caractérisée en ce que les ouvertures d'échappement recouvrent radialement la section transversale des entredents de la couronne.
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 EP0254077A2 (fr) 1988-01-27
EP0254077A3 EP0254077A3 (en) 1988-03-09
EP0254077B1 true EP0254077B1 (fr) 1990-11-14

Family

ID=25845735

Family Applications (2)

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

Family Applications Before (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) EP0362906B1 (fr)
DE (2) DE3766177D1 (fr)
ES (2) ES2022841B3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102852787A (zh) * 2011-06-27 2013-01-02 株式会社山田制作所 油泵

Families Citing this family (25)

* 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
DE4107704C2 (de) * 1990-03-15 1994-12-01 Barmag Luk Automobiltech Hydraulikpumpe
IT1271052B (it) * 1993-11-18 1997-05-26 Pompa ad ingranaggi interni con sporgenze volumetriche
US6461118B1 (en) * 1997-07-18 2002-10-08 Rpm Industries, Inc. Oil pump by-pass valve for an internal combustion engine
US6544008B1 (en) * 1997-07-18 2003-04-08 John K. Apostolides Internal vent for reducing seal pressure in prelubrication pump assembly
US7137789B2 (en) * 1997-07-18 2006-11-21 Rpm Industries, Inc. Vent for reducing seal pressure in pump assembly
US6708710B1 (en) * 1997-10-30 2004-03-23 Rpm Industries, Inc. Vehicle fluid change apparatus and method
US6988506B1 (en) 1997-10-30 2006-01-24 Rpm Industries, Inc. Fluid transfer system
US7150286B2 (en) * 1997-10-30 2006-12-19 Rpm Industries, Inc. Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
US9062575B2 (en) * 1997-10-30 2015-06-23 RPM Industries, LLC Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
DE19804133A1 (de) * 1998-02-03 1999-08-12 Voith Turbo Kg Sichellose Innenzahnradpumpe
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
WO2006000181A1 (fr) * 2004-06-24 2006-01-05 Luk Automobiltechnik Gmbh & Co. Kg Pompe
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
CN102131673B (zh) * 2008-01-17 2015-06-17 费希尔动力有限公司 躺椅机构及座椅组件
DE102011089609A1 (de) * 2011-12-22 2013-06-27 Robert Bosch Gmbh Innenzahnradpumpe
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
CN117222813A (zh) * 2021-02-19 2023-12-12 1158992Bc有限公司 流体传输装置

Family Cites Families (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191509359A (en) * 1915-06-25 1916-06-22 Walter Elsworthy Lilly Improvements in or relating to Rotary Engines, Pumps, Meters, and Blowers.
US1863335A (en) * 1922-12-20 1932-06-14 Hill Compressor & Pump Company Rotary pump
DE409134C (de) * 1924-01-22 1925-02-02 Bbc Brown Boveri & Cie Verdichter oder Expansionskraftmaschine nach Art einer Zahnradpumpe
DE445893C (de) * 1924-03-14 1927-06-20 Hill Compressor & Pump Co Inc Verdichter mit umlaufenden Kolben
GB265511A (en) * 1926-10-30 1927-02-10 Sidney Zaleski Hall Improvements in and relating to rotary pumps
US1861155A (en) * 1929-06-07 1932-05-31 Harry Barker Screw pump
US2428181A (en) * 1944-10-27 1947-09-30 Frank C Sibley Rotary gear pump
FR912425A (fr) * 1945-02-26 1946-08-08 Compresseurs de fluides et ses applications
US2916999A (en) * 1956-05-25 1959-12-15 Gen Motors Corp Variable discharge vane pump
US2918009A (en) * 1957-02-01 1959-12-22 Dieny & Lucas Soc Nouv Injection-compressor apparatus
US2997227A (en) * 1958-12-17 1961-08-22 Bendix Westinghouse Automotive Unloader for rotary compressors
US3045778A (en) * 1960-03-10 1962-07-24 Roper Hydraulics Inc Lube pumping system
DE1426751A1 (de) * 1965-03-04 1968-11-21 Danfoss As Drehkolbenmaschine
AT291775B (de) * 1968-11-18 1971-07-26 Hohenzollern Huettenverwalt Hydraulische Zahnradmaschine
US4025243A (en) * 1973-01-05 1977-05-24 Gresen Manufacturing Company Orbital device
GB1457514A (en) * 1973-05-10 1976-12-01 Lucas Industries Ltd Gear pumps and motors
DE2421891A1 (de) * 1974-05-07 1975-11-20 Bosch Gmbh Robert Zahnradmotor
DE2425022A1 (de) * 1974-05-24 1975-12-04 Bosch Gmbh Robert Kolbenpumpe
CH591627A5 (fr) * 1975-12-19 1977-09-30 Rollstar Ag
DE2705256A1 (de) * 1977-02-09 1978-08-10 Bosch Gmbh Robert Zahnradmaschine (pumpe oder motor)
DE2720406A1 (de) * 1977-05-06 1978-11-09 Audi Nsu Auto Union Ag Inneneingriffszahnradpumpe vorzugsweise fuer brennkraftmaschinen in antriebsaggregaten von kraftfahrzeugen
DE2758376A1 (de) * 1977-12-28 1979-07-05 Schwaebische Huettenwerke Gmbh Kolbenkraft- oder -arbeitsmaschine mit innenlaeuferzahnradoelpumpe
DE2815362A1 (de) * 1978-04-10 1979-10-18 Bosch Gmbh Robert Hydraulikanlage
DE2920685A1 (de) * 1979-05-22 1980-12-04 Bosch Gmbh Robert Drucklufterzeugungsanlage
DE2933084A1 (de) * 1979-08-16 1981-03-26 Robert Bosch Gmbh, 70469 Stuttgart Drucklufterzeugungsanlage
DE3005657A1 (de) * 1980-02-15 1981-08-20 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Zahnradpumpe
US4480962A (en) * 1980-08-11 1984-11-06 Vickers, Incorporated Pump with inlet passages downstream and through its flow control valve
GB2104153B (en) * 1981-08-15 1984-08-30 Concentric Pumps Ltd Rotary positive-displacement fluid-pumps
DE3210759A1 (de) * 1981-09-17 1983-10-06 Walter Schopf Pumpenkombination mit mengenreguliereinrichtung
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
EP0173778B1 (fr) * 1984-09-05 1990-03-07 Hobourn Engineering Limited Pompes
GB2167130B (en) * 1984-11-19 1988-01-13 Hydrovane Compressor Rotary positive displacement air compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102852787A (zh) * 2011-06-27 2013-01-02 株式会社山田制作所 油泵
CN102852787B (zh) * 2011-06-27 2016-01-20 株式会社山田制作所 油泵

Also Published As

Publication number Publication date
EP0362906B1 (fr) 1991-09-04
US4813853A (en) 1989-03-21
EP0254077A3 (en) 1988-03-09
EP0254077A2 (fr) 1988-01-27
ES2022841B3 (es) 1991-12-16
EP0362906A3 (en) 1990-05-30
ES2024708B3 (es) 1992-03-01
DE3772775D1 (de) 1991-10-10
EP0362906A2 (fr) 1990-04-11
DE3766177D1 (de) 1990-12-20

Similar Documents

Publication Publication Date Title
EP0254077B1 (fr) Pompe à engrenages internes
DE3333647C2 (de) Schmiermittelpumpe für die Druckerzeugung bei einem druckumlaufgeschmierten Verbrennungsmotor
EP0712997B1 (fr) Pompe à engrenages internes avec réglage de l'aspiration
DE4425912A1 (de) Hydrodynamischer Strömungswandler
WO1993011376A1 (fr) Boite de vitesses a pompe volumetrique
DE3444859A1 (de) Rotationszellenpumpe fuer hydrauliksysteme
DE60031459T2 (de) Gerotormotor mit Schmiernuten
EP0225338B1 (fr) Pompe a capacite variable
EP0315878B1 (fr) Pompe à engrènement interne
EP0846861B1 (fr) Pompe annulaire à engrenages continuellement variable
DE3737961A1 (de) Innenzahnradpumpe
DE4421255C1 (de) Füllstücklose Innenzahnradpumpe
DE2437688B2 (de) Axialstellvorrichtung für eine parallel- und innenachsige Rotationskolbenmaschine
EP0475109B1 (fr) Pompe à engrenages internes pour fluide hydraulique
DE873208C (de) Drehkolbenpumpe
EP0244575B1 (fr) Pompe à engrenages internes
DE4440782C5 (de) Innenzahnradpumpe mit Verdrängervorsprüngen
EP0474001B1 (fr) Pompe à engrenages internes pour fluide hydraulique
DE3627414A1 (de) Verbrennungsmotor
DE3624517A1 (de) Innenzahnradpumpe
EP1764506A2 (fr) Pompe à engrenages internes
DE102010005984B4 (de) Regelölpumpe
DE3624382A1 (de) Exzentrische sperrschieberpumpe, insbesondere zur foerderung von schmierstoffen fuer antriebe
EP0473025A1 (fr) Pompe à engrenages internes pour fluide hydraulique
DE3603773A1 (de) Zahnradmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): CH DE ES FR GB IT LI SE

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): CH DE ES FR GB IT LI SE

17P Request for examination filed

Effective date: 19880722

17Q First examination report despatched

Effective date: 19890216

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE ES FR GB IT LI SE

XX Miscellaneous (additional remarks)

Free format text: TEILANMELDUNG 89122024.6 EINGEREICHT AM 27/06/87.

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3766177

Country of ref document: DE

Date of ref document: 19901220

ITTA It: last paid annual fee
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19930609

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 19930617

Year of fee payment: 7

Ref country code: CH

Payment date: 19930617

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19940628

Ref country code: ES

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 19940628

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19940630

Ref country code: CH

Effective date: 19940630

EUG Se: european patent has lapsed

Ref document number: 87109295.3

Effective date: 19950110

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

EUG Se: european patent has lapsed

Ref document number: 87109295.3

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 19990601

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20010608

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20010621

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20010710

Year of fee payment: 15

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020627

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030101

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20020627

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030228

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050627