EP0994257A1 - Aussenzahnradpumpe mit Fördervolumenbegrenzung - Google Patents
Aussenzahnradpumpe mit Fördervolumenbegrenzung Download PDFInfo
- Publication number
- EP0994257A1 EP0994257A1 EP99119067A EP99119067A EP0994257A1 EP 0994257 A1 EP0994257 A1 EP 0994257A1 EP 99119067 A EP99119067 A EP 99119067A EP 99119067 A EP99119067 A EP 99119067A EP 0994257 A1 EP0994257 A1 EP 0994257A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- pressure side
- external gear
- sealing surface
- 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
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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
-
- 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
- F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement
-
- 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
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
Definitions
- the invention relates to an external gear pump with a delivery volume limitation according to the Preamble of claim 1.
- the invention relates to one with increasing Speed self-regulating external gear pump.
- the invention has set itself the task of a To create external gear pump with delivery volume limitation, which is a to be promoted Pumps fluid as evenly as possible and pulsation-free.
- the invention is based on an external gear pump, which is in a housing has a rotationally driven gear pair with two intermeshing spur gears.
- the Gear pair is encased by housing surfaces, which together with axial sealing surfaces, over which the spur gears stroke with their end faces, delimit a conveying space that a low pressure side connected to a pump inlet and one High pressure side, which is connected to a pump outlet.
- To limit the Delivery volume of the pump is one of the spur gears on a piston that rotates together with this spur gear in the housing relative to the other spur gear is slidably received.
- the piston is preferably parallel to the axis of rotation of the spur gear mounted on the piston can be moved in a straight line.
- the length of engagement increases with increasing pump pressure, which depends on the Pump speed increases and decreases, automatically reduced.
- Limiting the Delivery volume or the automatic reduction of the pump with increasing Pump pressure is generated by applying fluid to the piston on the high-pressure side causes.
- the pressure force of the high pressure fluid acts the force of a restoring element opposite.
- the restoring element is preferably formed by a compression spring. The Pressurized fluid pushes the piston towards a reduction in the meshing length, and the restoring element counteracts this pressure force.
- the pump is preferably used as a lubricating oil pump, in particular for delivery of engine oil in reciprocating engines.
- this is in at least one axial sealing surface on a sealing web Sealing surface bordering a pocket or kidney formed that deepest an area Gear meshing of the gears with either the pump outlet or the pump inlet connects.
- the axial sealing surface borders directly on an end face of one of the Spur gears.
- the sealing web of the sealing surface covers the bottom of the tooth gap of the deepest Meshing of the two gears.
- the bag connects the tooth gap in the area of the deepest meshing with the next tooth gap on the high pressure side or Low pressure side.
- a sealing surface without a pocket is used to drain the High-pressure fluids taken care of from the tooth gap of deepest meshing.
- the depth of the pocket is preferably at most one fifth and at least one Twentieth of the maximum length of engagement of the two gears.
- Another bag also applies to this bag.
- their depths can be the same. Is on the high pressure side as well as on the Low pressure side of the sealing surface formed a pocket, so the pocket on the Low pressure side preferably to a shallower depth than the pocket on the High pressure side.
- the otherwise simply plane axial falls Sealing surface in a stair step from the easily flat pocket of constant depth.
- the maximum intervention length is at least with zero funding and corresponding to the Reset characteristic of the reset element in the lower speed range of the pump.
- the bag has an area, measured at the top of the bag, of at least 5% and at most 20% of the area covered by the spur gear.
- the Pocket surface is advantageously the friction between the sealing surface and the over the end face of the spur gear less.
- the pocket is preferably provided on the high-pressure side of the axial sealing surface, since in this case the displacement of fluid in the direction of delivery from the squeezing area of the closest meshing is facilitated.
- the bag can also be on the Low pressure side can be provided, since in this case the amount of fluid in the Squeeze area is reduced.
- the pump can also have several pairs of gears.
- a single Spur gear which is then preferably driven, with one or more Combing spur gears and in this way form several gear pairs of the pump.
- at least one pocket of the type described above is also the same Way in the area of deepest tooth engagement of this further gear pair or each further gear pairs are formed.
- this is also the case another spur gear to control the pump delivery volume by pressurization slidable relative to the common spur gear.
- the funding characteristics of Gear pairs are the same or differ from each other.
- Figure 1 shows an external gear pump with delivery volume limitation in one Longitudinal section, the position of which is shown in FIGS. 2 and 3 as section line C-C.
- a housing part 1 and a cover 2 screwed with it in a fluid-tight manner form a housing Pump.
- the housing part 1 and the cover 2 are each in an individual illustration in FIG. 2 or Figure 3 shown, to which reference should always be made. Also on that 5 is a perspective view of the cover 2 with the spur gear in place referred.
- the cover 2 has a cover plate and a circular cylindrical protruding therefrom Base 5 on.
- two spur gears 6 and 11 are parallel spaced axes of rotation.
- the spur gears 6 and 11 are located with their Gears 7 and 12 in a meshing engagement.
- a fluid inlet 3 which in FIG 1 is indicated in a dashed line, and at the pump inlet 3 opposite side of the spur gear pair a pump outlet 4.
- the rotary drive takes place via a drive shaft 8, which is in the base 5 of the cover 2 is pivoted.
- the spur gear 6 is secured against rotation and displacement on the drive shaft 8 attached.
- the other spur gear 11 is between two cylinder bodies 14 and 15 on one Shaft journal 13, which connects the two cylinder bodies 14 and 15 to one another, pivoted and not displaceable relative to the cylinder bodies 14 and 15.
- the two Cylinder bodies 14 and 15 form a piston which is in a bore in the housing part 1 can be moved back and forth along the alignment of the axis of rotation of the spur gear 11.
- This piston 14, 15 with fluid on the high pressure side becomes an outer first end face pressurized.
- the pump outlet 4 opens directly into a high-pressure chamber 18 that of the outer first end face of the piston 14, 15 or of the cylinder body 14 is sealed.
- the piston 14, 15 is by means of a Steel compression spring 20 is subjected to an elastic restoring force.
- the piston 14, 15 With an increase of the pressure in the high-pressure chamber 18, the piston 14, 15 becomes counter to the restoring one Force of the compression spring 20 relative to the spur gear 6 axially parallel in such a direction shifted that the length of engagement of the two spur gears 6 and 11 is reduced.
- the delivery volume of the pump is reduced as the engagement length is reduced.
- the engagement length corresponds to the length of the two equal lengths Spur gears. It is achieved with zero delivery, especially when the pump is at a standstill; the spur gears 6 and 11 face each other at the same height.
- the fluid delivery from the pump inlet 3 to the pump outlet 4 is carried out by a Pump delivery chamber, the outer surfaces of the housing part 1 around the tip circles Spur gears 6 and 11 around and of axial sealing surfaces 9, 10, 16 and 17 tight is enclosed and in which the pump inlet 3 and a connecting channel to Pump outlet 4 each open to one side of spur gears 6 and 11.
- axial sealing surfaces 9, 10, 16 and 17 are those surfaces of the housing 1, 2 or of the piston 14, 15 understood, the respective end faces of the spur gears 6 and 11 directly lie close together. They seal the pump delivery chamber in the axial direction and separate its low pressure side and high pressure side from each other or prevent one Short circuit.
- the axial sealing surfaces 9 and 10 are for the rotary drive Spur gear 6 shown in a plan view.
- the axial sealing surface 9 is free End face of the base 5 of the cover 2 is formed.
- the base 5 is also in one in FIG Shown view on the sealing web 21.
- the axial sealing surface 10 becomes opposite formed in the housing part 1.
- Top views of the axial sealing surfaces 16 and 17 for the Spur gear 11 are included in Figure 4.
- the axial sealing surface 9 is an annular surface with an outer diameter that the Diameter of the tip circle of the spur gear 6 corresponds. It has a simple plane Surface in which a pocket 22 and 23 are incorporated on both sides of a sealing web 21 is.
- the sealing web 21 protrudes into the tooth gap of the deepest meshing of the spur gears 6 and 11 and represents the separation of the Low pressure side and the high pressure side safely over the tooth mesh.
- the pockets 22 and 23 are open towards the outer peripheral edge of the axial sealing surface 9. They are each characterized by two control edges at an angle to each other, on which the axial Sealing surface 9 slopes vertically or slightly beveled towards the respective pocket 22 and 23, limited.
- the depths T1 and T2 of the pockets 22 and 23 and the height of their control edges is at least one twentieth and at most one fifth of the maximum length of the Engagement of the spur gears 6 and 11.
- the pockets 22 and 23 are of theirs Control edges simply flat up to their open edges.
- the depth T2 of the pocket 23 on the low pressure side is preferably less than the depth T1 of the pocket 22 on the High pressure side.
- T1 is one eighth and T2 is one tenth maximum engagement length of the spur gears 6 and 11.
- the one exempted from pocket 22 Area is compared to the recessed area of the pocket 23 at the same length of the Sealing web 21 delimiting control edge is larger because of the angle to the sealing web 21 extending second control edge at the pocket 22 at an obtuse angle to the control edge on Sealing web 21 runs as the corresponding control edge of the pocket 23.
- the pocket 22 covers a longer one from the outer peripheral edge of the axial sealing surface 9 Edge portion as the pocket 23.
- the pockets 25 and 26 of the opposite sealing surface 10 (FIG. 2).
- the pockets 22 and 25 of the same shape are located High pressure side and the same shape pockets 23 and 26 of the low pressure side of the Pump delivery room exactly opposite.
- the cylinder body 14 and 15 are individually in plan views of their axial Sealing surfaces 16 and 17 and each shown in a longitudinal section.
- the cylinder body 15 is additionally in a plan view of its outer end face facing the compression spring 20 pictured.
- the cylinder body 14 sealing the high-pressure chamber 18 is not on it illustrated, the end face facing the high-pressure chamber 18 simply flat.
- At the outer lateral surface is in the region of its sealing web 27 over the entire length of the Cylinder body 14 except a cylinder segment.
- the teeth of the Spur gears 6 and 11. serve as an anti-rotation device for the Pistons 14, 15 by the cylinder body 14 thus sliding along the base 5.
- the formation of the axial sealing surface 16 with the sealing web 27 and in particular the Formation of the pockets 28 and 29 corresponds to that of the axial sealing surface 9 and their pockets.
- the cylinder body 15 On its outer end face facing away from the spur gear 11 the cylinder body 15 is designed as a ring pot with a circumferential ring channel, the serves as a guide for the compression spring 20.
Abstract
Description
- Figur 1
- eine Außenzahnradpumpe mit Fördervolumenbegrenzung in einem Längsschnitt,
- Figur 2
- ein Gehäuseteil der Pumpe in der Draufsicht A-A der Figur 1,
- Figur 3
- einen Deckel der Pumpe in der Draufsicht B-B der Figur 1,
- Figur 4
- zwei Zylinderkörper, zwischen denen ein Stirnrad der Pumpe nach Figur 1 drehgelagert ist, und
- Figur 5
- eine perspektivische Ansicht des Deckels der Pumpe nach Figur 3 mit Stirnrad.
Claims (8)
- Außenzahnradpumpe mit Fördervolumenbegrenzung, die Pumpe umfassenda) ein Gehäuse (1, 2),b) wenigstens ein drehangetriebenes Zahnradpaar mit zwei in Eingriff befindlichen Stirnrädern (6, 11), die mit Mantelflächen des Gehäuses (1, 2) und axialen Dichtflächen (9, 10, 16, 17) einen Förderraum bilden, der eine mit einem Pumpeneinlass (3) verbundene Niederdruckseite und eine mit einem Pumpenauslass (4) verbundene Hochdruckseite aufweist, undc) einen Kolben (13, 14, 16), der als Drehlagerung für ein Stirnrad (11) des Zahnradpaars dient und zur Begrenzung des Fördervolumens der Pumpe zusammen mit diesem Stirnrad (11) durch Beaufschlagung mit Fluid der Hochdruckseite gegen die Kraft eines Rückstellelements (20) relativ zu dem anderen Stirnrad (6) des Zahnradpaars verschoben wird,
dadurch gekennzeichnet, dassd) in wenigstens einer axialen Dichtfläche (9) an einen Dichtsteg (21) der Dichtfläche (9) grenzend wenigstens eine Tasche (22; 23) ausgebildet ist, die einen Bereich tiefsten Zahneingriffs der Stirnräder (6, 11) mit entweder dem Pumpenauslass (4) oder dem Pumpeneinlass (3) verbindet. - Außenzahnradpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Tasche (22) in der axialen Dichtfläche (9) auf der Hochdruckseite des Förderraums ausgebildet ist und den Bereich tiefsten Zahneingriffs der Zahnräder (6, 11) mit dem Pumpenauslass (4) verbindet.
- Außenzahnradpumpe nach dem vorhergehenden Anspruch, dadurch gekennzeichnet, dass in der axialen Dichtfläche (9) auf der Niederdruckseite des Förderraums an den Dichtsteg (21) grenzend eine weitere Tasche (23) ausgebildet ist, die den Bereich tiefsten Zahneingriffs der Zahnräder (6, 11) mit dem Pumpeneinlass (3) verbindet.
- Außenzahnradpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Tasche (23) in der axialen Dichtfläche (9) auf der Niederdruckseite des Förderraums ausgebildet ist und den Bereich tiefsten Zahneingriffs der Zahnräder (6, 11) mit dem Pumpeneinlass (3) verbindet.
- Außenzahnradpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass eine maximale Länge des Zahneingriffs der Stirnräder (6, 11) das Fünf- bis Zwanzigfache der Tiefe der Tasche (22; 23) beträgt.
- Außenzahnradpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Tasche (22), auf der Höhe der Dichtfläche (9) gemessen, eine Fläche einnimmt, die 5 % bis 20 % einer Fläche ausmacht, die von dem an die Dichtfläche (9) grenzenden Stirnrad (6) überstrichen wird.
- Außenzahnradpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass jede der axialen Dichtflächen (9, 10, 16, 17) je einen Dichtsteg (21, 24, 27, 30) mit daran grenzenden Taschen (22, 25, 28, 31) auf der Hochdruckseite des Förderraums aufweist.
- Außenzahnradpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass jede der axialen Dichtflächen (9, 10, 16, 17) je einen Dichtsteg (21, 24, 27, 30) mit daran grenzenden Taschen (23, 26, 29, 32) auf der Niederdruckseite des Förderraums aufweist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19847132 | 1998-10-13 | ||
DE19847132A DE19847132C2 (de) | 1998-10-13 | 1998-10-13 | Außenzahnradpumpe mit Fördervolumenbegrenzung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0994257A1 true EP0994257A1 (de) | 2000-04-19 |
EP0994257B1 EP0994257B1 (de) | 2002-02-06 |
Family
ID=7884301
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99119067A Expired - Lifetime EP0994257B1 (de) | 1998-10-13 | 1999-09-30 | Aussenzahnradpumpe mit Fördervolumenbegrenzung |
Country Status (6)
Country | Link |
---|---|
US (1) | US6283735B1 (de) |
EP (1) | EP0994257B1 (de) |
JP (1) | JP2000120559A (de) |
AT (1) | ATE213054T1 (de) |
DE (2) | DE19847132C2 (de) |
ES (1) | ES2172279T3 (de) |
Cited By (3)
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---|---|---|---|---|
DE10033950C2 (de) * | 2000-07-13 | 2003-02-27 | Schwaebische Huettenwerke Gmbh | Pumpe mit Magnetkupplung |
US8376724B2 (en) | 2007-05-21 | 2013-02-19 | Tbk Co., Ltd. | Gear pump enabling efficient pump capacity change |
CN105736350A (zh) * | 2016-05-06 | 2016-07-06 | 上海幸福摩托车有限公司 | 一种齿轮式变量机油泵测试装置 |
Families Citing this family (31)
Publication number | Priority date | Publication date | Assignee | Title |
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KR100535484B1 (ko) * | 1999-12-31 | 2005-12-07 | 현대자동차주식회사 | 오일 펌프 |
FR2837536B1 (fr) | 2002-03-20 | 2004-06-25 | Renault | Pompe a huile a cylindree modulable pour automobile |
DE10222131C5 (de) * | 2002-05-17 | 2011-08-11 | Schwäbische Hüttenwerke Automotive GmbH & Co. KG, 73433 | Verdrängerpumpe mit Fördervolumenverstellung |
AT413140B (de) * | 2003-03-28 | 2005-11-15 | Tcg Unitech Ag | Zahnradpumpe |
WO2005057013A1 (de) * | 2003-12-10 | 2005-06-23 | Dieter Voigt | Drehzahlabhängige druckregelung von ölpumpen |
WO2005100780A2 (en) * | 2004-04-09 | 2005-10-27 | Hybra-Drive Systems, Llc | Variable capacity pump/motor |
US7281376B2 (en) * | 2005-02-22 | 2007-10-16 | Hybra-Drive Systems, Llc | Hydraulic hybrid powertrain system |
US8215932B2 (en) * | 2004-04-09 | 2012-07-10 | Limo-Reid, Inc. | Long life telescoping gear pumps and motors |
US20070227802A1 (en) * | 2004-04-09 | 2007-10-04 | O'brien James A Ii | Hybrid earthmover |
AT500629B8 (de) * | 2004-05-27 | 2007-02-15 | Tcg Unitech Ag | Zahnradpumpe |
US7832997B2 (en) * | 2004-12-22 | 2010-11-16 | Magna Powertrain, Inc. | Variable capacity gerotor pump |
US8011910B2 (en) * | 2005-02-22 | 2011-09-06 | Limo-Reid, Inc. | Low noise gear set for gear pump |
DE102006011200B4 (de) | 2006-03-10 | 2014-11-13 | Schwäbische Hüttenwerke Automotive GmbH & Co. KG | Außenzahnradpumpe mit Entlastungstasche |
DE102006018124A1 (de) * | 2006-04-19 | 2007-10-25 | Schwäbische Hüttenwerke Automotive GmbH & Co. KG | Verstellbare Rotationspumpe mit Verschleißminderung |
JP5230971B2 (ja) * | 2006-08-15 | 2013-07-10 | 株式会社Tbk | ギヤポンプ |
US7717690B2 (en) | 2006-08-15 | 2010-05-18 | Tbk Co., Ltd. | Gear pump |
DE102007033146B4 (de) * | 2007-07-13 | 2012-02-02 | Schwäbische Hüttenwerke Automotive GmbH & Co. KG | Verstellventil für die Verstellung des Fördervolumens einer Verdrängerpumpe |
US20110129359A1 (en) * | 2009-11-30 | 2011-06-02 | Caterpillar Inc. | Variable output pump |
DE102010003574B4 (de) | 2010-03-31 | 2012-02-09 | Schwäbische Hüttenwerke Automotive GmbH | Pressverbund und Verfahren zur Herstellung eines Pressverbunds |
DE102010020299B4 (de) | 2010-05-12 | 2013-05-16 | Schwäbische Hüttenwerke Automotive GmbH | Pumpe mit Reibkupplungs-Drehzahlregelung |
BRPI1001768A2 (pt) * | 2010-05-24 | 2012-01-24 | Jose Luiz Bertazzolli | transmissão continuamente variável |
TWM396333U (en) * | 2010-08-18 | 2011-01-11 | Sai Ke Ai Luo Technology Co Ltd | Air condensate device |
US20120051950A1 (en) * | 2010-08-27 | 2012-03-01 | Chang Chun-Hsien | Engine oil pump provided automatic adjustment of oil supply amount |
DE102011005408B4 (de) | 2011-03-11 | 2014-02-13 | Schwäbische Hüttenwerke Automotive GmbH | Verfahren zur Herstellung einer Fügeverbindung in einer Pumpe oder eines Nockenwellen-Phasenstellers |
KR20140140011A (ko) * | 2013-05-03 | 2014-12-08 | 장순길 | 가변 용량형 기어 펌프 |
KR102003107B1 (ko) | 2015-08-12 | 2019-07-24 | 장순길 | 가변 용량 펌프 |
WO2017026639A1 (ko) * | 2015-08-12 | 2017-02-16 | 장순길 | 가변 용량 기어 펌프 |
CN105697970A (zh) * | 2016-04-08 | 2016-06-22 | 上海幸福摩托车有限公司 | 一种齿轮式变量泵 |
CN105782019B (zh) * | 2016-05-04 | 2018-09-04 | 邦语(上海)汽车技术有限公司 | 一种可变量齿轮泵 |
US10113546B2 (en) * | 2016-08-16 | 2018-10-30 | Caterpillar Inc. | Pump for an engine |
DE102017112699A1 (de) * | 2017-06-08 | 2018-12-13 | Schwäbische Hüttenwerke Automotive GmbH | Außenzahnradpumpe |
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US2149326A (en) * | 1937-04-27 | 1939-03-07 | George W Wilkin | Variable capacity gear pump |
US2354992A (en) * | 1941-11-11 | 1944-08-01 | Westinghouse Electric & Mfg Co | Gear pump |
GB781697A (en) * | 1955-04-14 | 1957-08-21 | Borg Warner | Improvements in or relating to gear type pumps |
DE3528651A1 (de) * | 1985-08-09 | 1987-02-19 | Rohs Hans Guenther Prof Dr Ing | Zahnradpumpe |
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US1458204A (en) * | 1923-06-12 | tibbetts | ||
DE698627C (de) * | 1934-10-31 | 1940-11-14 | Fritz Egersdoerfer | naelen, an deren Muendungen die von der Saugseite her kommenden Zahnluecken vorbeigehen |
US3669577A (en) * | 1970-01-02 | 1972-06-13 | Swan G Swanson | Variable high speed gear pump |
US4233005A (en) * | 1978-01-18 | 1980-11-11 | Lucas Industries Limited | Hydraulic gear pump with recesses in non-working gear flanks |
JPS5773880A (en) * | 1980-10-23 | 1982-05-08 | Nissan Motor Co Ltd | Variable capacity gear pump |
DE4121074A1 (de) * | 1991-06-26 | 1993-01-07 | Pierburg Gmbh | Aussenzahnradpumpe |
-
1998
- 1998-10-13 DE DE19847132A patent/DE19847132C2/de not_active Expired - Fee Related
-
1999
- 1999-09-30 AT AT99119067T patent/ATE213054T1/de not_active IP Right Cessation
- 1999-09-30 ES ES99119067T patent/ES2172279T3/es not_active Expired - Lifetime
- 1999-09-30 DE DE59900821T patent/DE59900821D1/de not_active Expired - Fee Related
- 1999-09-30 EP EP99119067A patent/EP0994257B1/de not_active Expired - Lifetime
- 1999-10-12 JP JP11290329A patent/JP2000120559A/ja active Pending
- 1999-10-13 US US09/417,370 patent/US6283735B1/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2149326A (en) * | 1937-04-27 | 1939-03-07 | George W Wilkin | Variable capacity gear pump |
US2354992A (en) * | 1941-11-11 | 1944-08-01 | Westinghouse Electric & Mfg Co | Gear pump |
GB781697A (en) * | 1955-04-14 | 1957-08-21 | Borg Warner | Improvements in or relating to gear type pumps |
DE3528651A1 (de) * | 1985-08-09 | 1987-02-19 | Rohs Hans Guenther Prof Dr Ing | Zahnradpumpe |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10033950C2 (de) * | 2000-07-13 | 2003-02-27 | Schwaebische Huettenwerke Gmbh | Pumpe mit Magnetkupplung |
US8376724B2 (en) | 2007-05-21 | 2013-02-19 | Tbk Co., Ltd. | Gear pump enabling efficient pump capacity change |
CN105736350A (zh) * | 2016-05-06 | 2016-07-06 | 上海幸福摩托车有限公司 | 一种齿轮式变量机油泵测试装置 |
CN105736350B (zh) * | 2016-05-06 | 2018-02-13 | 上海幸福摩托车有限公司 | 一种齿轮式变量机油泵测试装置 |
Also Published As
Publication number | Publication date |
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ES2172279T3 (es) | 2002-09-16 |
EP0994257B1 (de) | 2002-02-06 |
JP2000120559A (ja) | 2000-04-25 |
US6283735B1 (en) | 2001-09-04 |
DE59900821D1 (de) | 2002-03-21 |
DE19847132A1 (de) | 2000-04-27 |
ATE213054T1 (de) | 2002-02-15 |
DE19847132C2 (de) | 2001-05-31 |
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