[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

EP0362906B1 - Pompe à engrènement interne - Google Patents

Pompe à engrènement interne Download PDF

Info

Publication number
EP0362906B1
EP0362906B1 EP89122024A EP89122024A EP0362906B1 EP 0362906 B1 EP0362906 B1 EP 0362906B1 EP 89122024 A EP89122024 A EP 89122024A EP 89122024 A EP89122024 A EP 89122024A EP 0362906 B1 EP0362906 B1 EP 0362906B1
Authority
EP
European Patent Office
Prior art keywords
tooth
outlet
geared wheel
internal
outlet openings
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
EP89122024A
Other languages
German (de)
English (en)
Other versions
EP0362906A3 (en
EP0362906A2 (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
Priority to ES89122024T priority Critical patent/ES2024708B3/es
Priority to EP89122024A priority patent/EP0362906B1/fr
Publication of EP0362906A2 publication Critical patent/EP0362906A2/fr
Publication of EP0362906A3 publication Critical patent/EP0362906A3/de
Application granted granted Critical
Publication of EP0362906B1 publication Critical patent/EP0362906B1/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 according to the preamble of claim 1.
  • 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.
  • 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 into a common pressure channel, and all outlet openings of a group are closed by check valves with one exception, if any.
  • 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 3444859.
  • This internal gear pump has the special feature 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 cells that are sealed off from one another on the suction and pressure side 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 outlet openings be created 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, 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 outlet openings are guided beyond the base circle of the ring gear and the bottom of the tooth gaps is widened in a funnel shape by a corresponding bevel between the end face and the bottom of the tooth. This also results in a reduction in throttle losses.
  • 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 gives with its control edge the flow from the inlet 45 to the outlet 46 freely.
  • the pump forms - as shown in FIG. 1 - on the outlet side between the intermeshing teeth of the outer wheel 1 and the inner wheel 3 three cells which are closed in the circumferential and axial directions and which have been completely or partially filled with oil via the inlet channel 35.
  • three outlet openings 48.1, 48.3, 48.5 are introduced in the cover 33.
  • 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 an appropriate position, with sufficient circumferential directions also Sealing surfaces remain.
  • tooth space base 30 represents half the shell 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 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 above the opening 48.5 and corresponding channels 49, 52 directly connected to the outlet chamber.
  • 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. That means:
  • 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 tooth cells that are sealed off from one another, are produced in accordance with 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 torque between the inner wheel 3 and ring gear 1 (driving flanks), are smaller Coverage produced, 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. 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, it can happen 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 be used, for example, to measure the oil temperature or the temperature of a machine part, for example a piston. It is also possible to use a different measuring instrument, for example a speed counter, instead of the temperature sensor 62.
  • 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 will meet 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 very can be chosen over a large area and the outlet openings can also 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 (4)

1. Pompe à engrenage à denture intérieure, comprenant un pignon moteur (3) et une couronne (1) à denture intérieure, dans laquelle, côté refoulement, les flancs arrière des dents du pignon (flancs d'étanchéité du pignon) sont en contact avec les flancs conjugués correspondants des dents de la couronne (flancs d'étanchéité de la couronne), dans la zone entre le point d'intersection des cercles de tête et le point primitif de fonctionnement, avec un rapport de recouvrement égal ou supérieur à 2, de manière à former une multitude de cellules de dents fermées les unes vis-à-vis des autres, plusieurs de ces cellules de dents étant reliées chaque fois par au moins un orifice de refoulement à clapet antiretour au canal de refoulement commun, caractérisée par le fait que dans la mesure où elles se situent en dehors du cercle primitif de fonctionnement, les entredents de la couronne sont sensiblement élargies en section par rapport à l'enveloppante d'une dent de pignon et/ou que les orifices de refoulement sont légèrement plus petits que la section de dent de la couronne, en déduisant une faible bande d'étanchéité.
2. Pompe selon la revendication 1, caractérisée par le fait que les orifices de refoulement se trouvent entre la ligne d'action et le cercle périphérique de la couronne et débouchent près de la ligne d'action, en laissant seulement une surface d'étanchéité étroite.
3. Pompe selon la revendication 1 ou 2, caractérisée par le fait que sur la face frontale en regard des orifices de refoulement, le fond des entredents de la couronne est élargi en forme d'entonnoir, presque jusqu'à la périphérie de la couronne.
4. Pompe selon l'une des revendications 1 à 3, caractérisée par le fait que la section des entredents de la couronne est radialement recouverte par les orifices de refoulement.
EP89122024A 1986-07-19 1987-06-27 Pompe à engrènement interne Expired - Lifetime EP0362906B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
ES89122024T ES2024708B3 (es) 1986-07-19 1987-06-27 Bomba de rueda dentada interior
EP89122024A EP0362906B1 (fr) 1986-07-19 1987-06-27 Pompe à engrènement interne

Applications Claiming Priority (5)

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
EP89122024A EP0362906B1 (fr) 1986-07-19 1987-06-27 Pompe à engrènement interne

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP87109295.3 Division 1987-06-27

Publications (3)

Publication Number Publication Date
EP0362906A2 EP0362906A2 (fr) 1990-04-11
EP0362906A3 EP0362906A3 (en) 1990-05-30
EP0362906B1 true EP0362906B1 (fr) 1991-09-04

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 After (1)

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

Country Status (4)

Country Link
US (1) US4813853A (fr)
EP (2) EP0362906B1 (fr)
DE (2) DE3772775D1 (fr)
ES (2) ES2024708B3 (fr)

Families Citing this family (26)

* 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
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
US6461118B1 (en) * 1997-07-18 2002-10-08 Rpm Industries, Inc. Oil pump by-pass valve for an internal combustion engine
US9062575B2 (en) * 1997-10-30 2015-06-23 RPM Industries, LLC Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
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
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
JP4928447B2 (ja) * 2004-06-24 2012-05-09 ルーク アウトモービルテヒニーク ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディトゲゼルシャフト ポンプ
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
JP5795726B2 (ja) * 2011-06-27 2015-10-14 株式会社山田製作所 オイルポンプ
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
JP2024507549A (ja) * 2021-02-19 2024-02-20 １１５８９９２ ビー．シー．リミテッド 流体移送デバイス

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
DE3005657C2 (de) * 1980-02-15 1987-01-02 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

Also Published As

Publication number Publication date
EP0254077A3 (en) 1988-03-09
EP0362906A3 (en) 1990-05-30
ES2022841B3 (es) 1991-12-16
EP0362906A2 (fr) 1990-04-11
EP0254077B1 (fr) 1990-11-14
ES2024708B3 (es) 1992-03-01
EP0254077A2 (fr) 1988-01-27
US4813853A (en) 1989-03-21
DE3766177D1 (de) 1990-12-20
DE3772775D1 (de) 1991-10-10

Similar Documents

Publication Publication Date Title
EP0362906B1 (fr) Pompe à engrènement interne
DE102004003335B4 (de) Motorölsystem mit Verstellpumpe
EP0712997B1 (fr) Pompe à engrenages internes avec réglage de l'aspiration
DE3333647C2 (de) Schmiermittelpumpe für die Druckerzeugung bei einem druckumlaufgeschmierten Verbrennungsmotor
DE4425912A1 (de) Hydrodynamischer Strömungswandler
DE3444859A1 (de) Rotationszellenpumpe fuer hydrauliksysteme
EP0619430B1 (fr) Pompe à engrenage internes pour gamme de vitesses rotatives élévées
EP1461533B1 (fr) Pompe
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
DE4421255C1 (de) Füllstücklose Innenzahnradpumpe
DE3841238A1 (de) Antriebskupplungseinheit
DE3737961A1 (de) Innenzahnradpumpe
DE1553004B2 (de) Steuerdrehschiebereinrichtung an einer Rotationskolbenmaschine
DE2437688B2 (de) Axialstellvorrichtung für eine parallel- und innenachsige Rotationskolbenmaschine
EP0475109B1 (fr) Pompe à engrenages internes pour fluide hydraulique
DE2239727A1 (de) Zahnradpumpe
EP0474001B1 (fr) Pompe à engrenages internes pour fluide hydraulique
DE4440782C5 (de) Innenzahnradpumpe mit Verdrängervorsprüngen
EP0244575B1 (fr) Pompe à engrenages internes
EP0473025B1 (fr) Pompe à engrenages internes pour fluide hydraulique
EP1764506A2 (fr) Pompe à engrenages internes
DE3624517A1 (de) Innenzahnradpumpe

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

17P Request for examination filed

Effective date: 19891129

AC Divisional application: reference to earlier application

Ref document number: 254077

Country of ref document: EP

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

17Q First examination report despatched

Effective date: 19910214

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AC Divisional application: reference to earlier application

Ref document number: 254077

Country of ref document: EP

AK Designated contracting states

Kind code of ref document: B1

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

ET Fr: translation filed
REF Corresponds to:

Ref document number: 3772775

Country of ref document: DE

Date of ref document: 19911010

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2024708

Country of ref document: ES

Kind code of ref document: B3

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 NON-PAYMENT OF DUE FEES

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: 89122024.6

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: 89122024.6

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

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 19950712

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