CN101566150A - 具有增强的排出口的变排量叶片泵 - Google Patents

具有增强的排出口的变排量叶片泵 Download PDF

Info

Publication number
CN101566150A
CN101566150A CNA2009101373696A CN200910137369A CN101566150A CN 101566150 A CN101566150 A CN 101566150A CN A2009101373696 A CNA2009101373696 A CN A2009101373696A CN 200910137369 A CN200910137369 A CN 200910137369A CN 101566150 A CN101566150 A CN 101566150A
Authority
CN
China
Prior art keywords
pump
control ring
exhaust port
discharge
variable displacement
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
Application number
CNA2009101373696A
Other languages
English (en)
Other versions
CN101566150B (zh
Inventor
马修·威廉森
大卫·R·沙尔弗
切扎尔·塔纳苏卡
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.)
Hanang auto parts Canada Ltd.
Original Assignee
Magna Powertrain Inc
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=40934135&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=CN101566150(A) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Magna Powertrain Inc filed Critical Magna Powertrain Inc
Priority to CN201310478488.4A priority Critical patent/CN103541898B/zh
Priority to CN201310478662.5A priority patent/CN103541894B/zh
Publication of CN101566150A publication Critical patent/CN101566150A/zh
Application granted granted Critical
Publication of CN101566150B publication Critical patent/CN101566150B/zh
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • 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
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

一种具有增强的排出口的变排量叶片泵。所述增强的排出口减小当加压工作流体逆转其流动方向以进入排出口时将以其它方式出现在排出口中的高压区域。通过减小所述高压区域，减小泵的转子上的反向转矩，并提高泵的能量效率。在一实施方式中，用于泵控制环的枢轴从常规的位置沿径向向外定位，以允许排出凹口相邻于排出口形成在控制环中且延伸经过枢轴而到达泵出口。在第二实施方式中，排出凹口绕枢轴形成于控制环中，且在控制环上设置有密封件以便阻止加压工作流体经过控制环泄漏。在第三实施方式中，与形成在控制环中的排出凹口相邻地设置有第二排出口，且排出凹口中的加压工作流体能够通过与泵出口流体连通的第二排出口离开排出凹口。

Description

具有增强的排出口的变排量叶片泵
技术领域
本发明涉及一种变排量叶片泵。更具体地，本发明涉及一种包括被设计为用于提高泵的能量效率的增强的排出口的变排量叶片泵。
背景技术
直至目前为止，定排量泵已常规地用作为内燃发动机的润滑油泵。为了防止在某些工作条件下的可能有破坏性的润滑油过度供给，已使用减压阀或其它控制机构以便将过度供给的油从泵的出口按路线发送回储存器或泵入口。
尽管这种系统已被证明是可靠的并且经济的，但是这种系统存在如下缺点：能量被泵用来对仅由所述控制机构改变方向至泵入口或储存器的过度供给的油进行加压，且此能量被浪费掉，从而降低了泵的能量效率。
近来，已考虑将变排量叶片泵用作为内燃发动机的润滑油泵。通过设置适当的控制机构以改变泵的排量从而仅提供为发动机的正常工作所必要的加压润滑油的量，就不需要能量来对不需要的油进行加压，由此能够提高泵和内燃发动机的能量效率。
但是，变排量叶片泵的常规设计已被证明比所需的能量效率低，尤其在大排量工作条件下更是如此。
期望具有一种变排量叶片泵，所述变排量叶片泵相比常规的变排量叶片泵具有提高的工作能量效率。
发明内容
本发明的目的在于提供一种新颖的变排量叶片泵，其消除或减轻了现有技术的至少一个缺点。
根据本发明第一方面，提供了一种变排量叶片泵，包括：转子，其具有一组沿径向延伸的叶片；控制环，其具有内表面，所述叶片抵靠所述内表面，相邻的叶片与所述控制环以及所述转子形成泵送室，且所述控制环能够绕枢轴运动以改变所述叶片的旋转中心与所述控制环的旋转中心之间的偏心距，从而改变所述泵的排量；进入口，用于从泵入口将工作流体引入至所述泵送室；排出口，其相对于所述转子的旋转方向定位于所述进入口的下游，以便将加压工作流体从所述泵送室传送至泵出口；以及排出凹部，其相邻于所述排出口形成在所述控制环的上表面和下表面中的至少一个中，并与所述排出口流体连通，以便形成增强的排出口。
本发明提供了一种包括增强的排出口的变排量叶片泵。所述增强的排出口为加压流体离开所述增强的排出口提供了附加的容积，并减小了当加压工作流体逆转其流动方向以进入所述排出口时将以其它方式出现在所述排出口中的高压区域。通过减小所述高压区域，减小了所述泵的转子上的反向转矩，并提高了所述泵的能量效率。在一个实施方式中，用于所述泵的控制环的枢轴从常规的位置沿径向向外定位，以允许排出凹部相邻于所述排出口形成在所述控制环中且延伸经过所述枢轴而到达所述泵出口。所述排出口与所述排出通道的组合形成增强的排出口。在第二实施方式中，所述排出凹部绕所述枢轴形成于所述控制环中，且在所述控制环上设置有密封件以便阻止加压工作流体经过所述控制环泄漏。在第三实施方式中，与形成在所述控制环中的所述排出凹部相邻地设置有第二排出口，且所述排出凹部中的加压工作流体能够通过与所述泵出口流体连通的所述第二排出口离开所述排出凹部。
附图说明
现在将参考附图仅以示例的方式对本发明的优选实施方式进行说明，在所述附图中：
图1示出了贯穿现有技术的变排量叶片泵的截面；
图2示出了图1中的泵的排出口部分的放大视图，其中示出了工作流体的流动；
图3示出了沿图1中的线3-3所截取的截面部分的立体图；
图4示出了贯穿根据本发明的变排量叶片泵的截面；
图5示出了沿图4中的线5-5所截取的截面部分的立体图；
图6示出了图4中的泵的排出口部分的放大视图，其中示出了工作流体的流动；
图7示出了贯穿根据本发明的另一变排量叶片泵的截面；
图8示出了图7中的泵的排出口部分的放大视图，其中示出了工作流体的流动；
图9示出了贯穿根据本发明的另一变排量叶片泵的截面；以及
图10示出了图9中的泵的排出口部分的放大视图，其中示出了工作流体的流动。
具体实施方式
现有技术的变排量叶片泵在图1中以20整体表示。泵20包括泵壳体24以及位于壳体24中的腔室32内的转子28。控制环36也定位于腔室32内，且控制环36绕枢轴40枢转，以便改变从转子28延伸的一组叶片44的偏心度，进而改变泵20的排量。
如本领域技术人员所公知，当转子28旋转(沿箭头48所指示的方向)时，来自与泵入口56相连的进入口52的工作流体被吸入形成于相邻的叶片44、转子28以及控制环36之间的泵室内。随着转子28的旋转，这些泵室中的每一个的容积首先增大，从而将工作流体从进入口52吸入泵室内，然后，当所述泵室与连接至泵出口64的排出口60形成流体连通时，所述泵室的容积减小。此减小的容积导致对供给至排出口60的工作流体进行加压。
通过使控制环36绕枢轴40枢转，能够改变叶片44的旋转中心与控制环36的旋转中心之间的偏心距，以便在泵的旋转期间改变泵室容积的变化，由此改变泵的排量。在图1中，泵20的控制环36处于其最大偏心位置，即，位于最大体积排量的位置点。
其中一种已知的对叶片泵的优化是在控制环36的上表面和下表面中与排出口60的最狭窄端部(即，下游端)相邻地设置被称为“泪滴状凹部”的凹部68。当转子28的旋转依次将每个叶片44移向排出口60的下游端时，加压工作流体必然经历方向的逆转以便离开排出口60，如图2中的箭头所示。
尽管凹部68提供了参与实现所述必要的工作流体的方向逆转的一些附加的流动区域，但是本发明人已判定，当工作流体经历方向逆转时，在排出口60的最狭窄端部72处会出现显著的压力增加。具体地，所述最狭窄端部72(在图3最清晰可见)有力地阻止了加压工作流体的必要逆转，从而导致显著的压力增加。此压力增加导致向转子28施加反向扭转力，并要求向转子28施加附加的输入转矩以克服所述反向转矩。
此外，随着凹部68的宽度必要地渐缩，使得凹部68终止于靠近枢轴40的76处以确保用于控制环36的足够的密封表面，通过此区域76的工作流体的流动受到限制，这也会促成所述压力增加和所述反向转矩。此外，由此引起的反向压力随工作流体的粘度而增加，因此尤其为泵所设定的大排量处启动和/或冷却工作条件将加剧所述反向转矩，
如本领域技术人员所显而易见的，提供用于抵消所述反向转矩所必需的输入转矩会在不能获得任何有益之处的情况下导致泵20所需的工作能量增加，由此降低泵20的整体能量效率。
根据本发明的变排量叶片泵的一种实施方式在图4、图5以及图6中以100整体表示。与现有技术的泵20相类似，泵100包括泵壳体104以及位于壳体104中的腔室112内的转子108。控制环116也定位于腔室112内，且控制环116绕枢轴120枢转，以便改变从转子108延伸的一组叶片124的偏心度，进而改变泵100的排量。
当转子108沿箭头128所指示的方向旋转时，工作流体经由与泵入口136流体连通的进入口132被引入至形成于相邻的叶片124、转子108以及控制环116之间的泵室。已在所述泵室内加压工作流体经由排出口140离开这些泵室，所述排出口140经由通道148与泵出口144流体连通。
与现有技术的泵20不同，在泵100中，控制环116包括与排出口140的最狭窄端部156相邻的排出凹部152。排出凹部152的径向宽度比可比较的现有技术的泪滴状凹部60大。此外，与泪滴状凹部不同，排出凹部152从排出口140的最狭窄端部156经过枢轴120朝向排出口140的上游端部和通道148延伸。在图5中可以清楚看出，以这种方式，排出口140和排出凹部152结合以便作用为增强的排出口。
为了容许排出凹部152的大的宽度和长的长度，将枢轴120相对于转子108的旋转中心沿径向向外移动，使得在与枢轴120相邻的控制环116的顶表面和底表面处仍旧有足够的材料可用于在控制环116与用于封闭室112的任意盖(例如图5所示的盖160)和/或室112的上表面和/或下表面之间提供密封表面。通过沿径向向外移动枢轴120以及通过设置排出凹部152，由此获得的增强的排出口的宽度158能够显著大于现有技术的泵20的排出口(如图3所示)。
图6示出了在泵100的增强的排出口中的如箭头所指示的工作流体的方向逆转。显而易见，在排出口140的最狭窄端部156处的排出凹部152的相对较大的宽度以及枢轴120的径向向外的设置导致容积的显著增加，在所述容积内，加压工作流体能够实现必要的方向改变。此外，通过使排出凹部152延伸经过枢轴120，避免了在从最狭窄端部156至通道148之间的加压工作流体的流动路径中的不适当的压缩。
由于排出通道152的设置，相比现有技术的泵20，使用泵100已获得能量效率的显著提高。
如本领域技术人员将显而易见的，排出通道152的截面不必是恒定的，但是优选要避免对经过排出通道152的工作流体的流动进行任何实质限制。此外，尽管在上述泵100的实施方式中，排出通道152形成于控制环116的上表面以及下表面中，但是也可以想到，在一些情况下，可能需要仅在控制环116的上表面或下表面中的一个中形成排出通道152。
图7示出了根据本发明的另一变排量叶片泵200。在泵200中，与泵100的部件大体相似的部件用相同的参考数字来表示。
在泵200中，与泵100的情况不同，不必将枢轴120从转子108的旋转中心沿径向向外移动。取而代之，泵200包括通道204，所述通道204将排出口140连接至泵出口144，其中，通道204的口部环绕枢轴120。控制环208以排出凹部212为特征，所述排出凹部212也环绕枢轴120。以这种方式，排出口140与排出凹部212结合以便作用为增强的排出口。
为了提供必要的密封以阻止加压工作流体从有效的排出口移至控制环208外部的腔室112，在控制环208上设置密封件216，且密封件216与腔室112中的密封表面220相接合。
如图8所示，排出凹部212的宽度和长度提供了相对较大的容积，在所述容积中，所述加压工作流体能够逆转方向并进入通道204，由此避免了不期望的高压区域，从而减小了转子108上的反向转矩并提高了泵200的能量效率。
图9示出了根据本发明的另一变排量叶片泵300。在泵300中，与泵100的部件大体相似的部件用相同的参考数字来表示。
在泵300中，控制环304形成有排出凹部308，所述排出凹部308罩盖住形成于腔室112中的第二排出口312。第二排出口312经由形成于泵壳体104中的一个或多个第二通道316与通道148流体连通。控制环304上的排出凹部308的上部示例和下部示例由另一个孔(在图9所示控制环304的位置上与第二排出口312共轴)互连，使得每个排出凹部308中的工作流体能够进入第二排出口312。可替代地，第二排出口312能够设置于泵壳体104中用于排出凹部308的下部示例，而另一第二排出口(未示出)能够设置于泵盖中用于排出凹部308的上部示例。
在图示实施方式中，第二通道316贯穿泵壳体104，但是，如本领域技术人员将理解的，第二通道能够以适当的方式形成，且能够形成于泵壳体104或泵盖(未示出)中。
进入排出凹部308的加压工作流体能够经由第二排出口312离开排出凹部308，并经由第二通道316到达通道148，以阻止与排出口140的下游端156相邻地形成高压区域。排出凹部308和第二排出口312与排出口140相结合而形成增强的排出口，并且如同泵100和泵200的情况一样，此增强的排出口减小了转子108上的反向转矩并提高了泵300的能量效率。
如图10所示，来自排出口140的加压工作流体能够进入第二排出口312，并流经第二通道316而到达通道148，然后到达泵出口144。
本发明提供了一种变排量叶片泵，其包括增强的排出口，所述增强的排出口减小了当加压工作流体逆转其流动方向以进入所述排出口时以不同方式出现在所述排出口中的高压区域。通过减小所述高压区域，减小了泵的转子上的反向转矩并提高了泵的能量效率。在一种实施方式中，将用于泵控制环的枢轴从常规位置沿径向向外定位，以允许排出凹部相邻于所述排出口形成在控制环中且延伸经过所述枢轴而到达所述泵出口。在第二实施方式中，排出凹部绕所述枢轴形成于所述控制环中，且在所述控制环上设置密封件以阻止加压工作流体经过所述控制环泄漏。在第三实施方式中，与形成于控制环中的排出凹部相邻地设置有第二排出口，且所述排出凹部中的加压工作流体能够通过与所述泵出口流体连通的所述第二排出口离开所述排出凹部。
本发明的上述实施方式意为本发明的示例，本领域技术人员在不背离由在此所附权利要求所单独限定的本发明的范围的情况下，可以对发明进行改变和修改。

Claims (5)

1.一种变排量叶片泵，包括：
转子，其具有一组沿径向延伸的叶片；
控制环，其具有内表面，所述叶片抵靠所述内表面，相邻的叶片与所述控制环以及所述转子形成泵送室，且所述控制环能够绕枢轴运动以改变所述叶片的旋转中心与所述控制环的旋转中心之间的偏心距，从而改变所述泵的排量；
进入口，用于从泵入口将工作流体引入至所述泵送室；
排出口，其相对于所述转子的旋转方向定位于所述进入口的下游，以便将加压工作流体从所述泵送室传送至泵出口；以及，
排出凹部，其相邻于所述排出口形成在所述控制环的上表面和下表面中的至少一个中，并与所述排出口流体连通，以便形成增强的排出口。
2.如权利要求1所述的变排量叶片泵，其中，所述排出凹部从所述排出口的下游端向上游延伸至所述枢轴的上游。
3.如权利要求1所述的变排量叶片泵，其中，所述排出凹部的径向宽度避免相邻于所述枢轴的实质限制。
4.如权利要求1所述的变排量叶片泵，其中，所述排出凹部向上游延伸且绕所述枢轴与所述泵出口流体连通，并且所述控制环设置有密封件以阻止加压工作流体经过所述控制环泄漏。
5.如权利要求1所述的变排量叶片泵，其中，所述排出凹部与第二排出口流体连通，所述第二排出口与所述泵出口流体连通。
CN200910137369.6A 2008-04-25 2009-04-24 具有增强的排出口的变排量叶片泵 Active CN101566150B (zh)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201310478488.4A CN103541898B (zh) 2008-04-25 2009-04-24 具有增强的排出口的变排量叶片泵
CN201310478662.5A CN103541894B (zh) 2008-04-25 2009-04-24 具有增强的排出口的变排量叶片泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US4780108P 2008-04-25 2008-04-25
US61/047,801 2008-04-25

Related Child Applications (2)

Application Number Title Priority Date Filing Date
CN201310478488.4A Division CN103541898B (zh) 2008-04-25 2009-04-24 具有增强的排出口的变排量叶片泵
CN201310478662.5A Division CN103541894B (zh) 2008-04-25 2009-04-24 具有增强的排出口的变排量叶片泵

Publications (2)

Publication Number Publication Date
CN101566150A true CN101566150A (zh) 2009-10-28
CN101566150B CN101566150B (zh) 2014-08-20

Family

ID=40934135

Family Applications (3)

Application Number Title Priority Date Filing Date
CN201310478488.4A Active CN103541898B (zh) 2008-04-25 2009-04-24 具有增强的排出口的变排量叶片泵
CN200910137369.6A Active CN101566150B (zh) 2008-04-25 2009-04-24 具有增强的排出口的变排量叶片泵
CN201310478662.5A Active CN103541894B (zh) 2008-04-25 2009-04-24 具有增强的排出口的变排量叶片泵

Family Applications Before (1)

Application Number Title Priority Date Filing Date
CN201310478488.4A Active CN103541898B (zh) 2008-04-25 2009-04-24 具有增强的排出口的变排量叶片泵

Family Applications After (1)

Application Number Title Priority Date Filing Date
CN201310478662.5A Active CN103541894B (zh) 2008-04-25 2009-04-24 具有增强的排出口的变排量叶片泵

Country Status (5)

Country Link
US (1) US8118575B2 (zh)
EP (1) EP2112379B2 (zh)
KR (1) KR101590187B1 (zh)
CN (3) CN103541898B (zh)
CA (1) CA2664067C (zh)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103890399A (zh) * 2011-10-18 2014-06-25 株式会社Tbk 叶片式液压装置
CN104870820A (zh) * 2012-12-20 2015-08-26 皮尔伯格泵技术有限责任公司 润滑油叶片泵
CN106939886A (zh) * 2016-01-04 2017-07-11 熵零技术逻辑工程院集团股份有限公司 流体机构及应用其的系统

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9181803B2 (en) 2004-12-22 2015-11-10 Magna Powertrain Inc. Vane pump with multiple control chambers
TR201819627T4 (tr) * 2004-12-22 2019-01-21 Magna Powertrain Usa Inc Değişken kapasiteli pompayı çalıştırmaya yönelik yöntem.
US8297943B2 (en) * 2006-11-06 2012-10-30 Magna Powertrain, Inc. Pump control using overpressure source
EP2443338A1 (en) * 2009-06-17 2012-04-25 Green Partners Technology Holdings Gmbh Rotary vane engines and methods
DE102010023068A1 (de) * 2010-06-08 2011-12-08 Mahle International Gmbh Flügelzellenpumpe
DE102011011690A1 (de) * 2011-02-18 2012-08-23 GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) Verstellbare Flügelzellenpumpe mit einem Ausnehmungen aufweisenden Schieber
EP2716912A1 (en) 2012-10-08 2014-04-09 Magna International Japan Inc. Balanced pressure dual pump
EP2735740B1 (en) * 2012-11-27 2018-01-24 Pierburg Pump Technology GmbH Variable displacement lubricant vane pump
US10113427B1 (en) 2014-04-02 2018-10-30 Brian Davis Vane heat engine
KR101662553B1 (ko) * 2015-09-11 2016-10-06 현대자동차주식회사 베인펌프
US20200080555A1 (en) * 2018-09-12 2020-03-12 GM Global Technology Operations LLC Variable Displacement Pump
CN111771059B (zh) * 2019-01-31 2024-01-12 斯泰克波尔国际工程产品有限公司 集成在泵的枢轴销中的应急阀

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4342545A (en) * 1978-07-24 1982-08-03 General Motors Corporation Variable displacement pump
US5090881A (en) * 1989-12-27 1992-02-25 Toyoda Koki Kabushiki Kaisha Variable-displacement vane-pump
US5178525A (en) * 1990-01-09 1993-01-12 Nissan Motor Co., Ltd. Variable volume type vane pump with lubricating oil reservoir
DE10018749A1 (de) * 2000-04-15 2001-10-25 Iav Gmbh Mengenregelbare Flügelzellenpumpe
US6457946B2 (en) * 1999-12-23 2002-10-01 Daimlerchrysler Ag Regulatable pump

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2651994A (en) 1946-12-12 1953-09-15 Houdaille Hershey Corp Variable capacity pump with dual discharge means
US2786422A (en) * 1952-12-15 1957-03-26 New York Air Brake Co Vane pump with improved discharge port
US2775946A (en) 1953-03-02 1957-01-01 George H Hufferd Constant delivery variable pressure pump
US2799995A (en) 1954-04-13 1957-07-23 Vickers Inc Power transmission
DE2300525A1 (de) 1973-01-05 1974-07-11 Albert A Schmitz Pumpe mit veraenderbarem foerdervolumen und umkehrbarer foerderrichtung
US4183723A (en) 1975-04-30 1980-01-15 Sundstrand Corporation Rotary vane pump having multi-independent outputs due to stator surfaces of different contour
JPH01262394A (ja) * 1988-04-12 1989-10-19 Diesel Kiki Co Ltd 可変容量型圧縮機
DE4011671C2 (de) 1990-04-11 1994-04-28 Glyco Metall Werke Regelbare Flügelzellenpumpe
DE4200305C2 (de) 1992-01-09 1995-06-08 Glyco Metall Werke Regelbare Flügelzellenpumpe in kompakter Bauweise
US5538400A (en) 1992-12-28 1996-07-23 Jidosha Kiki Co., Ltd. Variable displacement pump
US5738500A (en) 1995-10-17 1998-04-14 Coltec Industries, Inc. Variable displacement vane pump having low actuation friction cam seal
JPH09273487A (ja) 1996-04-08 1997-10-21 Jidosha Kiki Co Ltd 可変容量形ポンプ
US6503068B2 (en) 2000-11-29 2003-01-07 Showa Corporation Variable capacity type pump
JP3922878B2 (ja) 2000-12-04 2007-05-30 株式会社ジェイテクト 可変容量形ポンプ
JP2003021077A (ja) 2001-07-06 2003-01-24 Showa Corp 可変容量型ポンプ
US6558132B2 (en) 2001-09-24 2003-05-06 General Motors Corporation Variable displacement pump
JP4146312B2 (ja) 2003-07-25 2008-09-10 ユニシア ジェーケーシー ステアリングシステム株式会社 可変容量形ポンプ
CA2565179C (en) * 2004-05-07 2014-01-21 Magna Powertrain Inc. Vane pump using line pressure to directly regulate displacement
CA2581123C (en) 2004-09-20 2015-07-07 Magna Powertrain Inc. Pump with selectable outlet pressure
KR101235988B1 (ko) * 2004-10-25 2013-02-21 마그나 파워트레인 인크. 용적 변화 링 상의 힘을 감소시키는 챔버를 갖는 가변 용량베인 펌프
TR201819627T4 (tr) * 2004-12-22 2019-01-21 Magna Powertrain Usa Inc Değişken kapasiteli pompayı çalıştırmaya yönelik yöntem.
US8444395B2 (en) * 2006-01-31 2013-05-21 Magna Powertrain, Inc. Variable displacement variable pressure vane pump system
US20070224067A1 (en) 2006-03-27 2007-09-27 Manfred Arnold Variable displacement sliding vane pump
JP2008111360A (ja) 2006-10-30 2008-05-15 Showa Corp 可変容量型ポンプ
JP2008128024A (ja) 2006-11-17 2008-06-05 Hitachi Ltd 可変容量形ベーンポンプ
US7862306B2 (en) 2007-02-06 2011-01-04 Gm Global Technology Operations, Inc. Pressure regulating variable displacement vane pump

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4342545A (en) * 1978-07-24 1982-08-03 General Motors Corporation Variable displacement pump
US5090881A (en) * 1989-12-27 1992-02-25 Toyoda Koki Kabushiki Kaisha Variable-displacement vane-pump
US5178525A (en) * 1990-01-09 1993-01-12 Nissan Motor Co., Ltd. Variable volume type vane pump with lubricating oil reservoir
US6457946B2 (en) * 1999-12-23 2002-10-01 Daimlerchrysler Ag Regulatable pump
DE10018749A1 (de) * 2000-04-15 2001-10-25 Iav Gmbh Mengenregelbare Flügelzellenpumpe

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103890399A (zh) * 2011-10-18 2014-06-25 株式会社Tbk 叶片式液压装置
CN104870820A (zh) * 2012-12-20 2015-08-26 皮尔伯格泵技术有限责任公司 润滑油叶片泵
CN104870820B (zh) * 2012-12-20 2016-10-12 皮尔伯格泵技术有限责任公司 润滑油叶片泵
US9909584B2 (en) 2012-12-20 2018-03-06 Pierburg Pump Technology Gmbh Lubricant vane pump
CN106939886A (zh) * 2016-01-04 2017-07-11 熵零技术逻辑工程院集团股份有限公司 流体机构及应用其的系统

Also Published As

Publication number Publication date
CA2664067C (en) 2016-09-27
CN103541894B (zh) 2015-12-23
US20090269232A1 (en) 2009-10-29
KR20090113228A (ko) 2009-10-29
CN101566150B (zh) 2014-08-20
EP2112379A2 (en) 2009-10-28
CN103541894A (zh) 2014-01-29
US8118575B2 (en) 2012-02-21
EP2112379A3 (en) 2015-02-18
EP2112379B2 (en) 2022-01-19
CN103541898A (zh) 2014-01-29
KR101590187B1 (ko) 2016-01-29
CA2664067A1 (en) 2009-10-25
EP2112379B1 (en) 2018-08-15
CN103541898B (zh) 2015-11-18

Similar Documents

Publication Publication Date Title
CN101566150B (zh) 具有增强的排出口的变排量叶片泵
US8535030B2 (en) Gerotor hydraulic pump with fluid actuated vanes
US8419392B2 (en) Variable displacement vane pump
CN101253329B (zh) 具有改进进口通道的齿轮泵
CN107304765B (zh) 在密封座中包括润滑槽的旋转泵
US8348645B2 (en) Balanced pressure, variable displacement, dual lobe, single ring, vane pump
US7841846B2 (en) Vane pump with improved internal port placement
US11754071B2 (en) Hermetic compressor including an intermediate plate having a curved suction passage
CN111094749B (zh) 泵装置
CN215292888U (zh) 旋转式压缩机
US4498853A (en) Vane-type compressor
EP3828415B1 (en) Internal gear pump
US12018686B2 (en) Rotary compressor
CN112262259B (zh) 旋转式压缩机
US11773854B2 (en) Rotary compressor
US12098718B2 (en) Rotary compressor
US11891995B2 (en) Rotary compressor having improved vane chattering performance

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant
TR01 Transfer of patent right

Effective date of registration: 20210108

Address after: Ontario, Canada

Patentee after: Magna power systems FPC limited partnership

Address before: Ontario, Canada

Patentee before: MAGNA POWERTRAIN Inc.

TR01 Transfer of patent right
TR01 Transfer of patent right

Effective date of registration: 20210519

Address after: Ontario, Canada

Patentee after: Hanang auto parts Canada Ltd.

Address before: Ontario, Canada

Patentee before: Magna power systems FPC limited partnership

TR01 Transfer of patent right