EP3384159A1 - AUßENZAHNRADPUMPE - Google Patents
AUßENZAHNRADPUMPEInfo
- Publication number
- EP3384159A1 EP3384159A1 EP16805286.8A EP16805286A EP3384159A1 EP 3384159 A1 EP3384159 A1 EP 3384159A1 EP 16805286 A EP16805286 A EP 16805286A EP 3384159 A1 EP3384159 A1 EP 3384159A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- gear
- conveyor
- tooth flank
- external gear
- gear pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 67
- 230000005534 acoustic noise Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 230000008092 positive effect Effects 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000002776 aggregation Effects 0.000 description 1
- 238000004220 aggregation Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000003313 weakening effect Effects 0.000 description 1
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
- 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
- F04C2/20—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 dissimilar tooth forms
-
- 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
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
- F04C15/0049—Equalization of pressure pulses
-
- 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
Definitions
- the invention relates to an external gear pump having a driving first conveying gear and one of the first conveying gear
- the external gear pump serves to convey the fluid from its suction side to the pressure side.
- the fluid or its state of aggregation can be chosen arbitrarily, but it is preferably liquid under normal operating conditions of the external gear pump.
- External gear pump has a plurality of conveyor gears, namely the first conveyor gear and the second conveyor gear.
- Feed gear is preferably driven directly.
- it is for this purpose connected to a drive shaft of the external gear pump, in particular rigid and / or permanent.
- the second conveyor gear is indirectly driven by the drive shaft, namely via the first conveyor gear.
- the two gears each have a plurality of teeth, which engage in one another in dependence on the rotational angle position of the conveyor gears and cooperate for conveying the fluid from the suction side to the pressure side.
- Each tooth of the conveyor gears has over the leading tooth flank and the trailing tooth flank, wherein the
- Vorertonschweflanke in the direction of rotation of the respective conveyor gear is front, so the tooth is limited to the front or in the direction of rotation, while the trailing tooth edge is present in the direction of rotation behind, and thus limits the tooth to the rear or against the direction of rotation.
- the leading tooth flank of at least one tooth of the first feed gear comes into abutting contact with the trailing tooth flank of a tooth of the second feed gear.
- the second conveyor gear is driven by the first conveyor gear.
- the gear pump includes a driving gear and a driven gear.
- the driving gear has symmetrical teeth while the driven gear has asymmetrical teeth.
- Asymmetric teeth of the driven gear include working surfaces which have a profile which corresponds to the profile of the working and non-working surfaces of the driving gear, but they have one
- Non-working surface which is substantially free, so that it is substantially planar.
- the driving gear and the driven gear have non-contact surfaces, which are formed substantially flat to form an even larger dead space and to prevent a cavitation phenomenon when the teeth in axial
- Blistering can be cavitation phenomena essentially exclude which could occur at high pump speeds.
- the trailing tooth flanks of the first feed gear or the trailing tooth flanks of the teeth of the first feed gear, in particular all the teeth of the first feed gear, have a special configuration. In each case, there is a fluid pocket in each of the trailing tooth flanks. This results from the fact that the corresponding trailing tooth flank is at least partially concave, that is to say has a curvature engaging in the circumferential direction in the corresponding tooth.
- the trailing tooth flank is curved in the direction of an engagement flank of the tooth.
- the vault is in radial direction, ie in a cross section through the first
- the fluid pocket is present at the at least one axial position.
- the fluid pocket does not necessarily the entire first conveyor gear or the entire
- Trailing tooth edge penetrates in the axial direction, although this may of course be the case.
- the fluid pocket passes only partially through the first conveying gear or the trailing tooth flank in the axial direction, that is, at least on one side in the axial direction at the edge in the first conveying gear or its trailing tooth flank.
- first conveying gear and the second conveying gear have the same gear parameters.
- Gear parameters are, for example, the root diameter, the pitch circle diameter, the tip diameter, the gear pitch, the head height, the foot height, the tooth width, the pitch, the number of teeth and / or the module to understand. Preference is given to the conveyor gears
- the teeth of the conveyor gears can basically have any type of toothing, which, however, for the two
- Conveyor gears coincide.
- Veriereungsart involute a Zykloidenveriereung or a
- the inlet pressure is on the suction side and the outlet pressure on the pressure side. Due to the higher pressure or the larger pressure ratio results in a very high efficiency, in particular a higher efficiency than in an external gear pump, in which the Nachlaufbergerflanken not concave to form the fluid pockets.
- Pressure ratio is achieved in particular in the range of constant promotion of the external gear pump, in which the pressure, namely the
- the Abregelmatiiere is that speed from which the two conveyor gears are displaced in the axial direction against each other to reduce their coverage. For example, lie the
- Down the speed range may be limited by a minimum speed of the external gear pump.
- the minimum speed corresponds for example to an idling speed of a drive unit
- Drive device is and, for example, the promotion of a fluid for the drive unit is used.
- the external gear pump is as
- Invention of course also directed to a drive device, in particular for a motor vehicle, which has a drive unit, such as an internal combustion engine, and an external gear pump, in particular according to this description.
- the drive unit is supplied by means of the external gear pump a fluid conveyed by this, wherein the fluid is for example a lubricant or the like.
- a preferred embodiment of the invention provides that the teeth of the first conveyor gear are designed symmetrically. This is to be understood in particular that seen in cross section the
- Trailing tooth edge is formed symmetrically to the leading tooth flank, so that the tooth having the leading tooth flank and the trailing tooth flank is symmetrical with respect to a longitudinal center plane.
- the second conveyor gear has an unchanged toothing, in particular without fluid pockets, throughout.
- the fluid pocket in the respective trailing tooth flank of the first conveying gear seen in the axial direction at least on one side, in particular only on one side, is open-edged.
- the fluid pocket preferably only partially penetrates the first conveying gear or the trailing tooth flank in the axial direction. Accordingly, it is, for example, seen open in the axial direction on only one side.
- an embodiment of the external gear pump can be realized, in which the fluid pocket completely engages through the first conveying gear or the trailing tooth flank in the axial direction, so that the fluid pocket is open on both sides seen in the axial direction.
- trailing tooth flanks of the first conveying gear each have a fluid pocket region receiving the fluid pocket and a contact region adjoining directly to the fluid pocket region, the trailing tooth flanks being convex in the contact region, in particular symmetrical to the respective leading tooth flanks of the corresponding advancing tooth flanks Teeth are. In such an embodiment, so engages through the
- Fluid pocket the first conveyor gear in the axial direction only partially.
- the fluid pocket lies in the fluid pocket area of the
- the contact region preferably forms a wall delimiting the fluid pocket, which lies in a plane perpendicular to the axis of rotation or only encloses a small angle therewith.
- the low angle For example, it may not exceed 20 °, not more than 15 °, not more than 10 °, not more than 5 °, not more than 2,5 ° or not more than 1 °.
- Contact area run the Nachlaufschwflanken in contrast to the fluid pocket area convex, so are curved in the circumferential direction to the outside, ie away from the respective leading tooth flank of the corresponding tooth.
- the trailing tooth flank of each of the teeth seen in cross section runs symmetrically to the corresponding leading tooth flank of the tooth.
- the cross section of the trailing tooth flank, in particular of the entire tooth of the first conveying gear having the trailing tooth flank is preferably the same in the axial direction in the region of the fluid pocket, that is to say in the fluid pocket region. This may additionally or alternatively also apply to the contact area.
- first conveyor gear and the second conveyor gear in the axial direction with respect to a rotational axis of the conveyor gears against each other to set a certain coverage are displaced, the dimensions of the contact area in the axial direction are chosen such that the Contact area at each position of the two conveyor gears to each other in the axial direction in registration with the second
- Feed gear is present.
- the specific coverage can be the
- the delivery volume flow is greater, the greater the overlap between the two conveyor gears in the axial direction.
- the first conveyor gear set in the axial direction and therefore only rotatable is stored, for example, in a pump housing the
- the second conveyor gear is rotatably mounted and displaceable in the axial direction, preferably also in the
- the displacement of the two conveyor gears may be limited so that they are always at least partially overlapping each other, so in any position of the conveyor gears to each other out of engagement.
- the contact area can be designed or its dimensions chosen such that, regardless of the position of the conveyor gears to each other, the contact area in the axial direction always in registration with the second
- Feed gear is present.
- External gear pump achieves excellent back-turning ability of the external gear pump.
- Feed gear in longitudinal section seen the contact area to at least 25%, at least 50%, at least 75% or at least 100%
- the second conveyor gear closes - again in longitudinal section - in the presence of the smallest possible coverage - flush with the contact area.
- a further preferred embodiment of the invention provides that a tooth flank wall region delimiting the fluid pocket of the respective
- Trailing tooth edge of the first conveyor gear starts directly from a Zahnfußschi, in particular tangentially expires from this.
- the tooth flank wall region is the region of the trailing tooth flank which bounds the fluid pocket in the circumferential direction.
- the Zahnfuß réelle lies in each case between two teeth of the first conveyor gear before or limits the teeth in the radial direction inwards.
- the Zahnfuß réelle is circular or circular section-shaped and lies over the entire circumference of the first conveyor gear on the
- the fluid pocket now preferably begins directly at the Zahnfuß Vietnamese, so seen in cross section at thepetit Vietnamese bemesser the first fraudzähnrads.
- the tooth flank region particularly preferably runs tangentially into the tooth root circle or proceeds tangentially therefrom. In this way, a particularly robust
- the teeth of the first conveyor gear each have a head portion in which the trailing tooth flank is convex, in particular is formed symmetrically to the corresponding leading tooth flank. It has already been pointed out above that the concave course of the trailing tooth flank does not necessarily have to be provided over its entire extent in the radial direction. Rather, the concave profile can extend only over part of the trailing tooth flank in the radial direction.
- the teeth of the first conveying gear each have a head region on which ends the concave profile of the respective trailing tooth flank.
- the concave course of the trailing tooth flank preferably extends as seen in cross-section from the tooth root circle to the head region.
- the trailing tooth flank is preferably convex, ie it is outward in the circumferential direction or arched from the same tooth associated Vorlaufiziflanke fort away.
- the trailing tooth flank is configured symmetrically to the leading tooth flank of the same tooth. This allows a high delivery volume flow or a high delivery pressure of the external gear pump, wherein the delivery pressure is the difference between a pressure on the pressure side and a pressure on the suction side.
- Difference between tip radius and root radius of the teeth of the first feed gear at least 5%, at least 10%, at least 15%, at least 20%, at least 25%, at least 30%, at least 35% or at least 40%. Seen in cross-section are the
- the dimensions of the head region correspond to the tip circle radius of the first feed gear minus the largest extension of the fluid pocket in the radial direction, again in cross section. If the dimensions of the head region are now based on the difference between the tip circle radius and the root circle radius, then the values given above preferably result.
- the tooth flank wall region is arcuate in cross section. This is seen in cross section at least partially, but preferably over the entire extent of the fluid pocket of the case.
- the tooth flank wall region adjoins the head region via a chamfer or a rounding.
- Tooth flank wall area and the head area is - so seen in cross section - so not abrupt. Rather, the chamfer or the rounding between the tooth flank region and the head region are again provided in cross-section, in order to ensure high strength of the tooth
- the rounding can in principle be chosen arbitrarily, for example, it has a radius which, based on the dimensions of the head region, is at least 0%, at least 5%, at least 2.5%, at least 1%, at least 0.5%, at least 0.25 % or at least 0.1%.
- the chamfer or the rounding are preferably part of the fluid pocket.
- FIG. 1 shows a region of an external gear pump, namely a first one
- Figure 3 is a cross-sectional view of the first conveyor gear, as well 4 shows a detailed representation of a region of the first conveyor gear.
- FIG. 1 shows a part of an external gear pump 1, namely a first conveying gear 2 and a second conveying gear 3.
- Feed gear 2 is designed as a driving conveyor gear, so it is directly driven.
- the second conveying gear 3 can only be driven indirectly via the first conveying gear 2.
- the first conveying gear 2 has teeth 5, while the second conveying gear 3 has teeth 6, of which only a few are exemplified.
- the conveyor gears 2 and 3 and their teeth 5 and 6 mesh with each other, so that during a rotational movement of the conveyor gears 2 and 3 in the direction of arrow 4, a fluid is conveyed from a suction side 7 to a pressure side 8 of the external gear pump 1.
- Each of the teeth 5 has a leading tooth flank 9 leading in the direction of rotation and a trailing trailing tooth flank 10. This is indicated only for one of the teeth 5.
- each tooth has 6 of the. second conveyor gear 3 via a front in the direction of rotation
- External gear pump 1 they are additionally in the axial direction, for example with respect to a rotation axis 3 of the first conveyor gear 2 or a rotational axis 14 of the second conveyor gear 3 against each other displaced.
- the first conveyor gear 2 is fixedly arranged in the axial direction, while the second conveyor gear 3 is displaceable in the axial direction. This is indicated by the double arrow 15.
- the conveyor gears 2 and 3 preferably have the same dimensions in the axial direction. Of course, however, different dimensions can be realized.
- Conveyor gear 2 for forming a respective fluid pocket 16 in the radial direction at least partially concave. That means in
- Conveyor gears 2 and 3 are mutually displaceable in the axial direction, a very fast decay behavior after a cold start a
- FIG. 2 shows the area of the external gear pump 1, that is to say the two conveyor gear wheels 2 and 3, in the case of a second axial position of FIG Feed gears 2 and 3 against each other.
- this is a position in which the overlap in the axial direction between the conveyor gears 2 and 3 is minimal.
- the conveyor gears 2 and 3 are, however, arranged such that they do not engage each other in any position. Rather, the teeth should be 5 and 6 in every possible
- the teeth 5 each only partially pass through, so in the axial direction are designed open edge only on one side.
- the trailing tooth flanks 10 each have a fluid pocket region 17 and a contact region 18. While in the fluid pocket region 17, the trailing tooth flank 10 extends concavely in the radial direction at least partially, in the contact region 18 the trailing tooth flank 10 is at least partially convex, that is, in the respective one
- Vorertonschweflanke 9 facing away curved direction.
- the trailing tooth flank 10 is symmetrical to the
- the dimensions of the contact region 18 in the axial direction are selected such that even in the position of the two conveyor gears 2 and 3 shown here, in which the minimum overlap exists, the contact region 18 is in register with the second conveyor gear 3.
- the contact area 18 should therefore be present in each position of the conveyor gears 2 and 3 in register with the second conveyor gear 3.
- Circumferential direction between the conveyor gears 2 and 3 realized independently of the overlap.
- the game can be zero.
- it is greater than zero and is for example based on one of the axes of rotation 7 and 13 at most 0.1 °, at most 0.25 °, at most 0.5 °, at most 0.75 °, at most 1 °, at most 2.5 ° or at most 5 °. It may also be between two of the stated values, that is to say, for example, at least 0.25 ° and at most 0.75 °.
- FIG. 3 shows a cross-sectional view of the first conveyor gear 2. It can be seen that the fluid pocket 16 in the circumferential direction of a
- Tooth flank edge portion 19 is limited.
- the tooth flank wall region 19 is seen in cross-section preferably circular arc-shaped.
- the tooth flank wall region 19 preferably extends from a tooth root circle 20, which is present in each case between two teeth 5 of the conveyor gear 2, up to a head region 21 of the respective tooth 5.
- the tooth root circle 20 has a root diameter d f .
- Tip diameter is indicated in the embodiment shown here as d k .
- the tooth height h is set for the embodiment of the external gear pump 1 shown here from a pocket height h t and a head area height h k of the head area 21 together. This in turn results in that the fluid pocket 16 in the radial direction directly adjoins the Zahnfuß Vietnamese 20.
- the fluid pocket 16 or the tooth flank wall region 19 delimiting the fluid pocket 16 starts directly from the tooth root circle 20. Preferably, it runs tangentially out of this.
- the tooth flank wall region 19 can be seen in cross-section i circular arc-shaped, in particular over its entire extent or at least a large part of its extension in the radial direction away, in particular, at least 50%, at least 75%, at least 80%, at least 85%, at least 90% or at least 100%.
- the tooth flank wall region 19 extends into the head region 21 or merges into it.
- the transition can be made for example via a rounding 22 in order to achieve a high strength of the first conveyor gear 2.
- the dimensions h k of the head portion 21 is based on half the difference between the tip circle diameter d k and the root diameter d f at least 5%, but may be larger. It can clearly be seen again here that the fluid pocket 16 only opens on one side open in the first
- Conveyor gear 2 is formed. Seen on one side in the axial direction, it is bounded by a wall 23 formed by the contact region 18.
- FIG. 4 shows a detailed representation of a region of the first
- the rounding 22 can be seen, via which the tooth flank wall region 19 merges into the head region 21.
- the rounding 22 may be part of the tooth flank wall region 19 or the head region 21.
- External gear pump 1 has an extremely low tendency to cavitate because fluid pushed into the fluid pocket 16 can at least partially escape from it in the axial direction. At the same time, however, the reverse rotation of the external gear pump 1 and a
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015015752 | 2015-12-04 | ||
PCT/EP2016/002007 WO2017092862A1 (de) | 2015-12-04 | 2016-11-28 | AUßENZAHNRADPUMPE |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3384159A1 true EP3384159A1 (de) | 2018-10-10 |
EP3384159B1 EP3384159B1 (de) | 2020-11-25 |
Family
ID=57471784
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16805286.8A Active EP3384159B1 (de) | 2015-12-04 | 2016-11-28 | Aussenzahnradpumpe |
Country Status (5)
Country | Link |
---|---|
US (1) | US10989190B2 (de) |
EP (1) | EP3384159B1 (de) |
CN (1) | CN108291537B (de) |
DE (1) | DE102016014175A1 (de) |
WO (1) | WO2017092862A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017102856A1 (de) | 2017-02-13 | 2018-08-16 | Schwäbische Hüttenwerke Automotive GmbH | Zahnrad mit Druckausgleichstasche |
CN109322821B (zh) * | 2018-10-09 | 2023-07-04 | 宿迁学院 | 一种用于消除齿轮泵径向力的组合结构 |
CN109268258B (zh) * | 2018-10-09 | 2023-07-07 | 宿迁学院 | 一种外啮合齿轮泵的//形卸荷槽 |
CN110748483A (zh) * | 2019-08-20 | 2020-02-04 | 无锡压缩机股份有限公司 | 一种螺杆压缩机主机降噪结构 |
CN114427532B (zh) * | 2022-01-27 | 2024-02-23 | 张义山 | 一种泵用降噪转子机构 |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US294026A (en) | 1884-02-26 | Rotary meter | ||
US1686867A (en) * | 1926-11-03 | 1928-10-09 | Lewis O Kuhn | Gear pump |
GB632462A (en) * | 1946-05-17 | 1949-11-28 | Bendix Aviat Corp | Improvements in or relating to gear pumps or motors |
US3709055A (en) * | 1971-01-04 | 1973-01-09 | L Grove | Gear tooth profile |
JPS50702B2 (de) | 1971-08-28 | 1975-01-10 | ||
GB1467441A (en) * | 1973-03-15 | 1977-03-16 | Lucas Industries Ltd | Hydraulic gear pumps and motors |
US3981646A (en) | 1973-03-15 | 1976-09-21 | Lucas Aerospace Limited | Gear pumps and motors |
DE2421891A1 (de) | 1974-05-07 | 1975-11-20 | Bosch Gmbh Robert | Zahnradmotor |
US4233005A (en) | 1978-01-18 | 1980-11-11 | Lucas Industries Limited | Hydraulic gear pump with recesses in non-working gear flanks |
SE429783B (sv) | 1981-12-22 | 1983-09-26 | Sullair Tech Ab | Rotorer for en skruvrotormaskin |
DE3809721C1 (de) | 1988-03-23 | 1989-06-01 | Robert Bosch Gmbh, 7000 Stuttgart, De | |
GB9702836D0 (en) * | 1997-02-12 | 1997-04-02 | Apv Uk Plc | Rotor for use in a rotary pump |
US6123533A (en) | 1997-04-22 | 2000-09-26 | Dana Corporation | Cavitation-free gear pump |
DE10140066A1 (de) | 2001-08-16 | 2003-02-27 | Volkswagen Ag | Zahnradpumpe |
HUE025067T2 (en) | 2002-06-03 | 2016-01-28 | M&M Tech Inc | Gear Pump |
DE10355214A1 (de) * | 2003-11-26 | 2005-06-30 | Robert Bosch Gmbh | Zahnradpumpe, insbesondere Kraftstoffpumpe |
WO2005119066A2 (en) * | 2004-06-04 | 2005-12-15 | Entek Manufacturing Inc. | Gear for use in a gear pump |
DE102006011200B4 (de) | 2006-03-10 | 2014-11-13 | Schwäbische Hüttenwerke Automotive GmbH & Co. KG | Außenzahnradpumpe mit Entlastungstasche |
US8490284B2 (en) * | 2009-10-09 | 2013-07-23 | Luren Precision Co., Ltd. | Gear and method for forming tooth profile thereof |
DE102010038430B4 (de) * | 2010-07-26 | 2012-12-06 | Schwäbische Hüttenwerke Automotive GmbH | Verdrängerpumpe mit Absaugnut |
JP5695995B2 (ja) | 2011-07-25 | 2015-04-08 | 株式会社神戸製鋼所 | ギアポンプ |
ITMI20122168A1 (it) * | 2012-12-18 | 2014-06-19 | Mario Antonio Morselli | Macchina idraulica a ingranaggi e relativa ruota dentata |
-
2016
- 2016-11-28 DE DE102016014175.1A patent/DE102016014175A1/de not_active Withdrawn
- 2016-11-28 WO PCT/EP2016/002007 patent/WO2017092862A1/de unknown
- 2016-11-28 EP EP16805286.8A patent/EP3384159B1/de active Active
- 2016-11-28 CN CN201680070594.0A patent/CN108291537B/zh active Active
- 2016-11-28 US US15/779,170 patent/US10989190B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
DE102016014175A1 (de) | 2017-06-08 |
WO2017092862A1 (de) | 2017-06-08 |
EP3384159B1 (de) | 2020-11-25 |
CN108291537B (zh) | 2020-10-09 |
US10989190B2 (en) | 2021-04-27 |
US20180347561A1 (en) | 2018-12-06 |
CN108291537A (zh) | 2018-07-17 |
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