US20120251370A1 - Internal gear pump - Google Patents

Internal gear pump Download PDF

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Publication number
US20120251370A1
US20120251370A1 US13/432,060 US201213432060A US2012251370A1 US 20120251370 A1 US20120251370 A1 US 20120251370A1 US 201213432060 A US201213432060 A US 201213432060A US 2012251370 A1 US2012251370 A1 US 2012251370A1
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US
United States
Prior art keywords
thrust ring
housing
cover portion
gear
gap
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.)
Abandoned
Application number
US13/432,060
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English (en)
Inventor
Franz Mayr
Michael Haid
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.)
Magna Steyr Fahrzeugtechnik GmbH and Co KG
Original Assignee
Steyr Daimler Puch Fahrzeugtechnik AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Steyr Daimler Puch Fahrzeugtechnik AG and Co KG filed Critical Steyr Daimler Puch Fahrzeugtechnik AG and Co KG
Assigned to MAGNA STEYR FAHRZEUGTECHNIK AG & CO KG reassignment MAGNA STEYR FAHRZEUGTECHNIK AG & CO KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HAID, MICHAEL, MAYR, FRANZ
Publication of US20120251370A1 publication Critical patent/US20120251370A1/en
Abandoned legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Q—ARRANGEMENT OF SIGNALLING OR LIGHTING DEVICES, THE MOUNTING OR SUPPORTING THEREOF OR CIRCUITS THEREFOR, FOR VEHICLES IN GENERAL
    • B60Q1/00—Arrangement of optical signalling or lighting devices, the mounting or supporting thereof or circuits therefor
    • B60Q1/26—Arrangement of optical signalling or lighting devices, the mounting or supporting thereof or circuits therefor the devices being primarily intended to indicate the vehicle, or parts thereof, or to give signals, to other traffic
    • B60Q1/2661—Arrangement of optical signalling or lighting devices, the mounting or supporting thereof or circuits therefor the devices being primarily intended to indicate the vehicle, or parts thereof, or to give signals, to other traffic mounted on parts having other functions
    • B60Q1/2669—Arrangement of optical signalling or lighting devices, the mounting or supporting thereof or circuits therefor the devices being primarily intended to indicate the vehicle, or parts thereof, or to give signals, to other traffic mounted on parts having other functions on door or boot handles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Q—ARRANGEMENT OF SIGNALLING OR LIGHTING DEVICES, THE MOUNTING OR SUPPORTING THEREOF OR CIRCUITS THEREFOR, FOR VEHICLES IN GENERAL
    • B60Q3/00—Arrangement of lighting devices for vehicle interiors; Lighting devices specially adapted for vehicle interiors
    • B60Q3/20—Arrangement of lighting devices for vehicle interiors; Lighting devices specially adapted for vehicle interiors for lighting specific fittings of passenger or driving compartments; mounted on specific fittings of passenger or driving compartments
    • B60Q3/267—Door handles; Hand grips

Definitions

  • the invention relates to an internal gear pump for delivering a fluid, in particular one of the gerotor pump type.
  • Such an internal gear pump has a driven gear wheel (also referred to as an inner rotor) and an annular gear (also referred to as an external rotor) interacting with the gear wheel, the annular gear having at least one tooth more than the gear wheel.
  • a driven gear wheel also referred to as an inner rotor
  • an annular gear also referred to as an external rotor
  • FIG. 7 illustrates a cross-sectional view of a conventional gerotor pump 101 (also referred to as an annular gear pump).
  • the pump 101 has a substantially cylindrical housing having an annular portion 103 .
  • An annular gear 105 is supported on the circular inner circumference of the annular portion 103 so that it is free to rotate about an axis A 1 .
  • a gear wheel 107 which is driven by way of a drive shaft (not shown) to rotate clockwise about an axis A 2 , for example, is arranged radially inside the annular gear 105 and eccentrically in relation to the annular gear 105 .
  • the gear wheel 107 has an external toothing
  • the annular gear 105 has an internal toothing with a greater number of teeth than that of the gear wheel 107 .
  • the gear wheel 107 meshes with the annular gear 105 and thereby drives the annular gear 105 to rotate. Owing to the greater number of teeth, however, the annular gear 105 rotates more slowly than the gear wheel
  • FIG. 7 Also illustrates in FIG. 7 are a suction port 109 and a pressure port 111 , which are formed on a base portion 113 of the pump housing, on which the annular gear 105 and the gear wheel 107 rest. Axially offset from the base portion 113 relative to the axes A 1 , A 2 , the annular gear 105 and the gear wheel 107 are covered by a cover portion of the housing (not shown). Due to the rotation of the gear wheel 107 relative to the housing (annular portion 103 , base portion 113 and cover portion), rotating pump chambers of variable volume, into which a fluid is drawn from the suction port 109 , are formed between the gear wheel 107 and the annular gear 105 . The fluid is finally expelled into a pressure chamber 115 of the pump 101 , into which the pressure port 111 opens or which is formed by the pressure port 111 itself.
  • German Patent Publication DE 43 15 432 A1 discloses the arrangement of a thrust ring, which is rotationally fixed to the rotating annular gear, between the gear wheel and the annular gear on the one hand and the cover portion of the housing on the other.
  • the thrust ring reduces the power loss by virtue of a reduction in the differential speed and hence a reduction in the friction.
  • the thrust ring may be composed of a material having a low coefficient of friction, or it may be provided with a coating of a material having a low coefficient of friction. This is comparatively costly, however, and even then still does not bring about the feasible reduction of the friction losses consistent with cost-effective manufacturing.
  • An object of the invention is to create an internal gear pump of said type, which being of simple construction exhibits a low degree of friction between the gear wheel and the annular gear on the one hand and the housing on the other.
  • a further object of the invention is to stabilize the alignment of the gear wheel.
  • an internal gear pump that includes at least the following: a thrust ring arranged between a gear wheel and an annular gear on the one hand and a cover portion of the housing on the other, at least one connecting passage on or in the housing of the pump extending from the delivery chamber of the pump up to a gap between the thrust ring and the cover portion of the housing, in order to carry fluid from the delivery chamber into the gap.
  • an internal gear pump that includes at least the following: a driven gear wheel; a rotatable annular gear operatively communicating with the driven gear wheel; a housing in which the driven gear wheel and the rotatable annular gear are arranged, the housing comprising a base portion, an annular portion and a cover portion, the base portion having a pressure port which forms a fluid delivery chamber; a thrust ring arranged between the driven gear wheel and the rotatable annular gear and also the driven gear wheel and the cover portion; a gap formed between the thrust ring and the cover portion; and at least one fluid connecting passage extending from the fluid delivery chamber up to the gap in order to carry fluid from the delivery chamber into the gap.
  • an internal gear pump that includes at least the following: a gear wheel which is rotatable about a first axis; an annular gear which is rotatable about a second axis; a thrust ring rotationally fixed to the annular gear; a housing which houses the gear wheel, the annular gear and the thrust ring, the housing having a fluid delivery chamber and a cover portion; a gap formed between the thrust ring and the cover portion; and a fluid connecting passage in the housing through which fluid flows from the fluid delivery chamber to the gap to thereby form a hydrodynamic lubricating film in the gap which reduces operational friction between the thrust ring and the cover portion.
  • an internal gear pump that includes at least the following: a gear wheel; an annular gear; a thrust ring; a housing having a fluid delivery chamber and a cover portion configured for placement such that a gap is formed between the thrust ring and the cover portion; and a fluid connecting passage through a fluid flows from the fluid delivery chamber to the gap to thereby form a hydrodynamic lubricating film in the gap which reduces operational friction between the thrust ring and the cover portion.
  • the fluid connecting passage has a first connecting groove in communication with the fluid delivery chamber, a second connecting groove in communication with the first connecting groove, and a third connecting groove in communication with the second connecting groove and the gap.
  • the thrust ring has a plurality of distribution grooves on a surface thereof which faces the gap and which are configured to distribute the fluid into the gap.
  • a gap is formed, which may extend over the entire surface of the thrust ring or merely a part thereof.
  • a connecting passage on or in the housing of the pump leads from the delivery chamber of the pump up to the gap, in particular right behind the thrust ring, when viewed from the base portion of the housing.
  • the pressurized fluid can therefore flow from the delivery chamber up to the gap, in order to build up a hydraulic pressure between the thrust ring and the cover portion of the housing and to form a hydrodynamically effective lubricating film as the thrust ring rotates.
  • the gap will only actually be formed by the pressurized fluid flowing in between the thrust ring and the cover portion of the housing.
  • the thrust ring may rest directly on the cover portion of the housing when the pump is at a standstill, when the pump is in operation it is important that a minimum clearance be provided between the thrust ring and the cover portion of the housing, in order to allow the formation of a fluid cushion or a lubricating film.
  • the fluid delivered by the pump is specifically carried along the connecting passage up to the gap between the rotor disc and the cover portion of the housing, the pressurized fluid, when necessary, being structurally configured to lift the thrust ring off slightly from the cover portion of the housing.
  • a further advantage consists in that feeding the pressurized fluid to the rear side of the thrust ring exerts a force, which serves to reduce or even avoid any tilting or wobbling of the gear wheel. Furthermore, the specifically diverted fluid serves for hydraulically centring the annular gear, thereby increasing the service life of the pump still further.
  • the thrust ring is preferably rotationally fixed to the annular gear.
  • the annular gear and the thrust ring may be integrally formed.
  • the thrust ring may also be rotatably coupled to the gear wheel, or the thrust ring is “floating,” that is to say, supported so that it is free to rotate.
  • a “base portion” of the housing this relates to the portion of the housing on which the pressure port is provided, which opens into the delivery chamber of the pump or which forms the delivery chamber.
  • a “cover portion” of the housing this relates to the portion of the housing on which the thrust ring rests.
  • the terms “base portion” and “cover portion” of the housing are used irrespective of whether the “base portion” in the pump installation position is arranged on an underside or an upper side of the pump, for example.
  • the connecting passage may be formed by one or more bores in the housing of the pump, for example, in particular by a bore in the base portion of the housing and/or by a bore in the annular portion of the housing.
  • the connecting passage includes at least one connecting groove, which extends along the inner circumference of the annular portion of the housing. It is therefore only necessary to apply a groove to the inside of the pump housing, for example by machining or by moulding, in order to carry the pressurized fluid up to the gap.
  • the connecting groove in the annular portion of the housing may extend, for example, up to the transition between the annular portion and the cover portion of the housing.
  • the connecting groove along the inner circumference of the annular portion of the housing preferably extends parallel to the axis of rotation of the annular gear.
  • the connecting groove may also be slanted at an angle conducive to the flow and need not necessarily have a rectilinear course.
  • Such an “axial” connecting groove may emerge directly from the delivery chamber of the pump.
  • a further connecting groove may be provided, which extends from the delivery chamber of the pump along the inside of the base portion of the housing up to the connecting groove in the annular portion of the housing, in particular radially outwards, in order to form a duct of L-shaped longitudinal section for the fluid.
  • the connecting passage (in particular the connecting groove in the annular portion of the housing) opens into an annular groove, which extends circumferentially along the transition between the annular portion and the cover portion of the housing and/or along the thrust ring.
  • This allows the pressurized fluid to be distributed along the circumference of the thrust ring and/or the cover portion of the housing, in order to penetrate into the gap between the thrust ring and the cover portion of the housing in multiple different angular positions, and therefore, to form a lubricating film that is as uniform as possible.
  • the cover portion of the housing includes at least one distribution groove, which extends radially inwards on the inside of the cover portion facing the thrust ring. This is particularly effective in conducting the fluid into the gap between the thrust ring and the cover portion of the housing, in order to form the desired lubricating film.
  • the respective distribution groove need not extend radially inwards in an exact straight line, other courses and alignments also being possible (for example, a slanting alignment, a laterally offset arrangement or a curved path with a component directed radially inwards).
  • the distribution groove preferably extends radially inwards starting from the transition between the annular portion and the cover portion of the housing and/or from the annular groove. A plurality of such distribution grooves are preferably provided.
  • the distribution groove in the cover portion of the housing it is preferred, in order to avoid additional leakage losses, if this groove has only a limited length, that is to say if the distribution groove does not extend radially inwards all the way through.
  • the distribution groove is in this case to be formed as a stepped groove. This is particularly important if the thrust ring and/or the cover portion of the housing has a central through-hole for a drive shaft. If additional leakage is required, however, it is alternatively advantageous if the distribution groove of the cover portion is continuous, that is to say if the distribution groove extends radially all the way inwards.
  • the thrust ring may also have at least one distribution groove, which extends radially inwards from the outer circumference of the thrust ring.
  • a distribution groove on the thrust ring also serves to enhance the distribution of the pressurized fluid inside the gap between the thrust ring and the cover portion of the housing, so that a more uniform build-up of pressure and a more efficient hydrodynamic lubrication is obtained.
  • the distribution groove in the thrust ring also need not be aligned radially inwards in an exact straight line, other courses and alignments being feasible.
  • the distribution groove in the thrust ring it is likewise possible for this to have a limited length, in order to reduce leakage losses in the radially inner area of the pump.
  • the distribution groove in the thrust ring may extend radially inwards all the way through, in order to bring about a specific leakage, as explained above in connection with the distribution groove in the cover portion of the housing.
  • the side of the thrust ring facing the cover portion of the housing may be of plane design. It is also advantageous, however, if the side of the thrust ring facing the cover portion of the housing is of tapered design, truncated cone-shaped design or convexly curved.
  • Such a shaping of the thrust ring is a simple way of ensuring that along the entire circumference a minimum gap always exists between the thrust ring and the cover portion of the housing, at least in a radially outer area, in order to ensure an efficient hydrodynamic lubrication.
  • the inside of the cover portion of the housing facing the thrust ring may also be of tapered design, truncated cone-shaped design or convexly curved.
  • distribution grooves may additionally be provided on the cover portion of the housing and/or on the thrust ring, in particular without or with specific leakage, as explained above.
  • the fluid in the case of such a specific leakage the fluid (particularly if the fluid is a lubricating oil) may be used for the lubrication of components close to the pump (for example through the use of a slinger ring).
  • the fluid may be carried out of the gap or directly out of the distribution groove to another component, which is arranged on or adjacent to the pump.
  • the housing of the pump may have an outlet port, in order to conduct a proportion of the fluid, carried out of the delivery chamber towards the gap, to another component and thereby to lubricate the latter.
  • the outlet port may, in particular, be provided in a radially inner area of the pump housing, for example, in the area of a central through-hole in the cover portion of the housing intended for a drive shaft.
  • a through-hole in the cover portion intended for a drive shaft need not be present in all embodiments of a pump in accordance with the invention.
  • the thrust ring extends in one piece in a radial direction between the gear wheel and the annular gear.
  • the thrust ring in accordance with this embodiment should at least partially cover not only the annular gear, but also the gear wheel in a radial direction, there being no possibility for direct communication of the gap (hydrodynamic lubrication gap between the thrust ring and the cover portion of the housing) with the pump chambers, which are formed between the gear wheel and the annular gear.
  • the thrust ring therefore ensures that no significant leakage losses occur in an axial direction (relative to the axis of rotation of the gear wheel and of the annular gear).
  • FIG. 1 illustrates a view in longitudinal section through an internal gear pump.
  • FIG. 2 illustrates a cross-sectional view of an internal gear pump.
  • FIGS. 3 a and 3 b illustrates a top view and a side view respectively of a thrust ring in accordance with embodiments.
  • FIG. 4 illustrates a top view of a thrust ring in accordance with embodiments.
  • FIG. 5 illustrates a view in longitudinal section through a thrust ring in accordance with embodiments.
  • FIG. 6 illustrates a view in longitudinal section through a thrust ring in accordance with embodiments.
  • FIG. 7 illustrates a cross-sectional view of a conventional internal gear pump.
  • FIG. 1 illustrates an internal gear pump 1 in accordance with the invention of the gerotor pump type.
  • the pump 1 includes a gear wheel 7 , which is driven to rotate about an axis A 2 by a shaft 17 passing through the pump.
  • the pump 1 further includes a freely rotatable annular gear 5 , that is to say an internal gear, the internal toothing of which meshes with the external toothing of the gear wheel 7 .
  • the axis of rotation A 1 of the annular gear 5 is eccentric to the axis of rotation A 2 of the gear wheel 7 .
  • a thrust ring 19 is rotationally fixed to the annular gear 5 , for example, via weld or bond. Alternatively, the thrust ring 19 is integrally formed with the annular gear 5 .
  • the thrust ring 19 may be composed, for example, of steel. Apart from a central through-hole for the shaft 17 , the thrust ring 19 is closed (that is to say it is without apertures) and is formed in one piece. The outside diameter of the thrust ring 19 corresponds to or is otherwise substantially equal to that of the annular gear 5 .
  • the gear wheel 7 , the annular gear 5 and the thrust ring 19 are accommodated in a housing of the pump 1 , which includes a hollow cylindrical annular portion 3 .
  • the annular gear 5 is rotatably supported on the inner circumference of the annular portion 3 .
  • the housing of the pump 1 further includes a base portion 13 , on which the gear wheel 7 and the annular gear 5 rest and which in the exemplary embodiment illustrated in FIG. 1 is integrally formed with the annular portion 3 .
  • a delivery chamber 15 of the pump 1 is formed in the base portion 13 of the housing
  • the housing of the pump 1 further includes a cover portion 21 , which in the exemplary embodiment illustrated in FIG. 1 takes the form of a separate cover.
  • the thrust ring 19 is arranged spatially between the gear wheel 7 and the annular gear 5 on the one hand and the cover portion 21 of the housing on the other.
  • a gap 23 of very narrow size is formed between the thrust ring 19 and the cover portion 21 .
  • the annular gear 5 and/or the thrust ring 19 may be pre-tensioned in an axial direction relative to the axes of rotation A 1 , A 2 (not illustrated).
  • the annular gear 5 When the pump 1 is in operation, the annular gear 5 , together with the thrust ring 19 coupled thereto, rotates more slowly than the gear wheel 7 .
  • the thrust ring 19 therefore contributes to a certain reduction of the friction losses, since the differential speed between the gear wheel 7 and the cover portion 21 is effectively reduced owing to the arrangement of the thrust ring 19 between the gear wheel 7 and the cover portion 21 of the housing.
  • a further reduction of the friction losses is achieved in the internal gear pump 1 in accordance with the embodiment illustrated in FIG. 1 in that a connecting passage on the housing of the pump 1 extends from the delivery chamber 15 up to the gap 23 between the thrust ring 19 and the cover portion 21 of the housing. Pressurized fluid is carried from the delivery chamber 15 along the connecting passage into the gap 23 , the fluid in the gap 23 forming a hydrodynamically effective lubricating film.
  • the connecting passage comprises a connecting groove 25 , which on the inside of the base portion 13 of the housing facing the annular gear 5 extends in a radial direction from the delivery chamber 15 up to the inner circumference of the annular portion 3 of the housing.
  • the radial connecting groove 25 is circumferentially closed by the underside of the annular gear 5 .
  • the radial connecting groove 25 opens into and is in communication with an axial connecting groove 27 of the connecting passage, and extends along the inner circumference of the annular portion 3 of the housing parallel to the axis of rotation A 1 of the annular gear 5 .
  • the axial connecting groove 27 is circumferentially closed by the outer circumference of the annular gear 5 .
  • the radial connecting groove 25 and the axial connecting groove 27 therefore, form a duct of L-shaped longitudinal cross-section as illustrated in FIG. 1 for the fluid of the pump 1 .
  • the connecting grooves 25 , 27 may form a cross-sectional aperture of between 1 to 5 mm 2 , for example, apertures of a different cross section naturally also being possible.
  • the suitable cross section generally depends on the output of the pump, the viscosity of the fluid and the pressure range of the pump.
  • the axial connecting groove 27 opens at the transition between the annular portion 3 and the cover portion 21 of the housing into a radial distribution groove 29 .
  • the radial distribution groove 29 is formed on the inside, that is to say, on the side of the cover portion 21 of the housing facing the thrust ring 19 , and which, extending radially inward, is of limited length.
  • a proportion of the fluid delivered by the pump 1 can pass or otherwise flow from the delivery chamber 15 into the gap 23 between the thrust ring 19 and the cover portion 21 of the housing, in order to form a hydrodynamically effective lubricating film in the gap 23 .
  • the lubricating film acts between the rotating thrust ring 19 and the fixed cover portion 21 of the housing.
  • the friction between the thrust ring 19 and the cover portion 21 of the housing is thereby considerably reduced. This contributes to a reduced wear and reduced heating and impairment of the fluid.
  • the cover portion 21 of the housing may obviously comprise a plurality distribution grooves 29 , particularly in a regular angular arrangement, in order to achieve a more uniform distribution of the fluid along the circumference of the thrust ring 19 .
  • a separate connecting passage, emerging from the delivery chamber 15 may be provided for each distribution groove 29 in the cover portion 21 .
  • an annular groove (not illustrated), which distributes the fluid delivered from the delivery chamber 15 along the connecting grooves 25 , 27 along the circumference of the thrust ring 19 or the cover portion 21 of the housing, may be provided on the annular portion 3 of the housing, on the cover portion 21 of the housing and/or along the outer circumference of the thrust ring 19 .
  • FIG. 2 illustrates a cross-sectional view of an internal gear pump in accordance with the invention.
  • FIG. 2 illustrates the radial connecting groove 25 in the base portion 13 and the axial connecting groove 27 in the annular portion 3 of the housing, which form the connecting passage described, extending from the delivery chamber 15 to the thrust ring 19 and the cover portion 21 of the housing.
  • one or more distribution grooves 31 may be provided on a surface of the rear side 33 of the thrust ring 19 facing the gap 23 (that is to say, on the upper side of the thrust ring 19 in the representation illustrated in FIG. 1 ).
  • a plurality if of radial distribution grooves 31 are provided, asymmetrically formed and arranged with a slight lateral offset.
  • the distribution grooves 31 in the thrust ring 19 are formed all the way through, that is to say they extend from the outer circumference up to the inner circumference (central through-hole for the shaft 17 ). In this way specifically desired leakage effects can be produced, for example, for a build-up of pressure, additional cooling or the lubrication of further components by leakage oil.
  • the distribution grooves 31 are formed as stepped grooves, which extend radially inwards only along a limited length from the outer circumference of the thrust ring 19 , for example, up to approximately 1 mm from the inner circumference of the thrust ring 19 . This serves to minimize leakage losses.
  • the rear side 33 of the respective thrust ring 19 is of plane design.
  • the rear side 33 of the thrust ring 19 facing the cover portion 21 of the housing may be of tapered design. This serves, as an alternative or addition to the provision of distribution grooves 31 , to bring about an enhanced distribution of the fluid delivered via the connecting passage.
  • the rear side 33 of the thrust ring 19 may have a bowed or arcuate design, that is to say, of convexly curved design. This serves, as an alternative or addition to the provision of distribution grooves 31 , to bring about an enhanced distribution of the fluid delivered via the connecting passage.
  • the inside surface of the cover portion 21 of the housing ( FIG. 1 ) facing the thrust ring 19 may be of tapered, truncated cone-shaped or convexly curved design.
  • the gap 23 between the thrust ring 19 and the cover portion 21 of the housing ( FIG. 1 ) has, at least in portions, an overall height diminishing radially inwards.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Arrangements Of Lighting Devices For Vehicle Interiors, Mounting And Supporting Thereof, Circuits Therefore (AREA)
  • Vehicle Interior And Exterior Ornaments, Soundproofing, And Insulation (AREA)
  • Rotary Pumps (AREA)
US13/432,060 2011-04-01 2012-03-28 Internal gear pump Abandoned US20120251370A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEDE10201101737 2011-04-01
DE102011001737A DE102011001737A1 (de) 2011-04-01 2011-04-01 Griffbauteil eines Kraftfahrzeuges

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US20120251370A1 true US20120251370A1 (en) 2012-10-04

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US13/432,060 Abandoned US20120251370A1 (en) 2011-04-01 2012-03-28 Internal gear pump
US13/436,345 Abandoned US20120314438A1 (en) 2011-04-01 2012-03-30 Handle Member For A Motor Vehicle

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EP (1) EP2505431B1 (es)
DE (1) DE102011001737A1 (es)
ES (1) ES2605996T3 (es)

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FR3049908B1 (fr) * 2016-04-12 2018-04-06 Renault S.A.S Console a poignee de maintien structurante
JP6546944B2 (ja) * 2017-02-16 2019-07-17 株式会社ニフコ グリップおよびグリップの作動機構
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JP7107735B2 (ja) * 2018-05-11 2022-07-27 株式会社アルファ 車両用ドア制御装置
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DE102011001737A1 (de) 2012-10-04
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ES2605996T3 (es) 2017-03-17
US20120314438A1 (en) 2012-12-13

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