WO2016026091A1 - 内燃机的机油泵 - Google Patents

内燃机的机油泵 Download PDF

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Publication number
WO2016026091A1
WO2016026091A1 PCT/CN2014/084743 CN2014084743W WO2016026091A1 WO 2016026091 A1 WO2016026091 A1 WO 2016026091A1 CN 2014084743 W CN2014084743 W CN 2014084743W WO 2016026091 A1 WO2016026091 A1 WO 2016026091A1
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WO
WIPO (PCT)
Prior art keywords
stator
oil pump
slider
combustion engine
internal combustion
Prior art date
Application number
PCT/CN2014/084743
Other languages
English (en)
French (fr)
Inventor
许仲秋
宋善国
刘光明
李战训
杨正中
Original Assignee
湖南机油泵股份有限公司
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 湖南机油泵股份有限公司 filed Critical 湖南机油泵股份有限公司
Priority to PCT/CN2014/084743 priority Critical patent/WO2016026091A1/zh
Priority to DE112014006869.1T priority patent/DE112014006869T5/de
Publication of WO2016026091A1 publication Critical patent/WO2016026091A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
    • F01M2001/0215—Electrical pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
    • F01M2001/0238—Rotary pumps

Definitions

  • the invention relates to the technical field of lubricating system of an internal combustion engine, and in particular to an oil pump of an internal combustion engine. Background technique
  • variable displacement vane pump is widely used in the lubrication of internal combustion engines due to its simple and reliable way of variable displacement and high total efficiency, so that a variable displacement vane type oil pump for an internal combustion engine has appeared.
  • the prior art vane type oil pump mainly includes a pump body, a pump cover, a stator, a rotor and a control mechanism, and its structure and principle are similar to those of the existing vane pump.
  • the operation mode is basically the same as that of the ordinary vane pump, so that the operation mode cannot be changed according to the actual working condition, so that the energy consumption and friction are not improved.
  • the technical problem to be solved by the present invention is to provide an oil pump for an internal combustion engine which can improve the operating condition according to actual working conditions to reduce energy consumption and improve friction.
  • a technical solution of the present invention is to provide an oil pump for an internal combustion engine having the following structure, comprising: a rotor assembly; a blade assembly coupled to the rotor assembly;
  • the stator assembly includes a stator and a slider, the stator is sleeved in the slider; when the blade assembly rotates synchronously with the rotor assembly, the stator and the slider are relatively rotatable.
  • the oil pump of the internal combustion engine of the present invention has the following advantageous effects as compared with the prior art. Since the blade assembly and the rotor assembly rotate substantially at the same time, the stator and the slider can rotate relative to each other, so that the operation mode of the stator can be divided into that the stator does not rotate, the stator and the blade rotate at the same speed, and the stator rotates relative to the slider, and the third is the stator. Rotate differentially with the n-plate. Therefore, one of the operation modes is selected according to the actual working conditions, for example, in the case where the internal torsion is short and the external torque is similar, the stator and the blades are differentially operated.
  • stator can move in this case, the surface of the stator and the wear of the blades are reduced, thereby ensuring the performance and reliability of the pump.
  • rotation of the stator reduces the friction between the stator and the blade and between the stator and the slider. Since the blades are driven by an engine or the like, the friction condition is improved and the energy consumption is also reduced.
  • the stator is a ring structure
  • the slider is concentric and clearance fit with the stator.
  • the stator carries the functions of the stator and the slider S in the present invention, and is irregular in shape, and when it is subjected to special processing or processing of a specific material, the processing difficulty is increased, and the cost is also greatly increased.
  • the stator in the present invention is a relatively regular ring structure, and therefore, it is convenient to perform special processing on the surface of the stator and Z or to use a special material. For example, steel is used to make the stator, or a quenching process is used to improve the quality of the stator. Therefore, the stator of the present invention can achieve better effects, such as better wear resistance, less damage, and the like. At the same time, it can reduce the processing difficulty and greatly reduce the processing cost.
  • the slider and stator are of different materials and surface treatments, and the slider and stator are relatively relatively high speed.
  • the slider and stator are processed according to the purpose and working needs of the slider and stator, which is beneficial to reduce the cost and at the same time improve the service life of the slider and the stator.
  • the blade assembly includes a locating ring and a plurality of blades at both ends, the blades being radially coupled to the outer circumferential faces of the two locating rings and extending in the direction of the stator assembly.
  • the S-position ring is used to connect and secure the blade, reducing the weight of the entire blade assembly.
  • the rotor assembly includes a drive shaft and a rotor, the rotor being uniformly provided with a groove or gap for receiving a tab; preferably, the rotor assembly is directly driven by a motor or a crankshaft.
  • the rotor assembly can also be driven indirectly.
  • the pump body of the oil pump further includes a rectangular sealing strip disposed outside the slider, and the rectangular sealing strip forms a closed variable feedback cavity with the rotational positioning arc of the slider. Since the eccentricity of the stator changes, a better seal can be formed by the rectangular seal.
  • the slider overcomes the elastic force of the variable elastic member attached thereto to cause the stator to rotate or move to change the displacement.
  • This feature applies not only to single-chamber feedback, but also to the fluid medium in the variable feedback chamber, which can be either oil or water or other fluids.
  • the stator in the case where the internal torque is small and the external torque is large, the stator does not rotate.
  • the external torque is significantly greater than the internal torque, the internal torque is insufficient to overcome the external torque and the stator does not rotate. This situation is basically the same as a conventional vane pump.
  • the stator and the blade rotate at the same speed, and the stator rotates at a high speed with respect to the slider.
  • the internal torque is significantly greater than the external torque, and the driving force can be provided to drive the stator to rotate in addition to the external torque.
  • the stator and the blade rotate at the same speed due to the action of the force and the reaction force.
  • the resistance and friction experienced are mainly between the outer surface of the stator and the slider. Since the blade is firmly attached to the inner surface of the stator, it is less prone to wear and leakage, so the oil pump can work reliably.
  • the stator, rotor and blades are differentially rotated with the internal torque being comparable to the magnitude of the external torque. This is the case where the internal torque is approximately equal or substantially equal to the external torque. This situation is between the case where the stator does not rotate and the stator and the blades rotate at the same speed. Less energy consumption and less friction, so it is an ideal operation Turn state. In addition, since the force and friction between the blade and the stator are relatively small and in contact with each other, the reliability during operation is high. Appendix
  • Fig. 1 is a schematic view showing the structure of an oil pump of an internal combustion engine of the present invention when a pump cover is not installed.
  • Figure 2 is a schematic view showing the split structure of some of the components in Figure 1. detailed description
  • 1 shows a specific embodiment of an oil pump of an internal combustion engine of the present invention.
  • 1 is a schematic diagram showing the internal structure of the oil pump of the internal combustion engine when the pump cover is not installed.
  • the oil pump of the internal combustion engine mainly includes a pump body, a rotor assembly 2, a blade assembly 3, a stator assembly 4, and a pump cover (not shown).
  • the drive shaft rotor assembly 2, the blade assembly 3 and the stator assembly 4 are all disposed in the cavity of the pump body 1.
  • the pump body 1 and the pump cover are sealed and connected by fasteners.
  • the rotor assembly 2 is driven directly by a motor or a crankshaft.
  • the prior art stator needs to have the function of a slider, the structure thereof is relatively complicated, and the complicated stator structure requires a special treatment method to improve the quality of the stator surface, such as steam treatment. Even so, the surface quality of the stator in the prior art is limited.
  • the treatment layer obtained by steam treatment is thin, and is easily worn quickly during operation to affect the performance of the oil pump.
  • the blade is stuck. Due to the complicated external structure of the stator, the frictional resistance is large, which damages the stator surface and causes the oil pump to fail.
  • the stator assembly 4 mainly includes an annular stator 6 and an irregularly shaped slider 9. The stator 6 is sleeved in the slider 9.
  • stator 6 and the slider 9 are in a clearance fit.
  • This structure is equivalent to dividing the stator of the prior art which has the functional characteristics of the slider into two parts, the stator 6 and the slider 9. Therefore, when the blade assembly 3 rotates with the rotor assembly 2, the stator 6 and the slider 9 are relatively rotatable.
  • the slider 9 and the stator 6 are subjected to different village materials and surface treatment processes, i.e., the performance of the slider 9 and the stator 6 can be improved, and the cost can be reduced as much as possible.
  • the rotor assembly 2 primarily includes a drive shaft 13 and a rotor 7.
  • the drive shaft 13 and the rotor 7 may be formed in one piece or in two parts and then assembled.
  • the drive shaft 13 is directly coupled to the output shaft or crankshaft of the motor to form a motor or crankshaft that directly drives the rotor assembly 2.
  • the outer surface of the rotor 7 is provided with a plurality of grooves or gaps 7.1.
  • the blade assembly 3 primarily includes a locating ring 8 and a plurality of n dies 10 at both ends.
  • the blades 10 are radially connected to the outer peripheral faces of the two positioning rings 8. In the axial direction, both ends of the blade 10 slightly protrude from the positioning ring 8 at both ends. In the radial direction, the vane 10 extends in the direction of the stator 6. When assembled, a plurality of blades 0 are fitted to the inner surface of the stator 6 in the radial direction of the moving blade 10, respectively.
  • the pump body 1 of the oil pump of the internal combustion engine of the present invention further includes a rectangular sealing strip disposed outside the slider 9. 11.
  • the rectangular sealing strip 1 is used together with the rubber rod 12.
  • the rectangular sealing strip 11 and the rotational positioning cam of the slider 9 form a closed variable feedback chamber 14.
  • the slider 9 overcomes the elastic force of the variable spring 5 acting on the outer surface of the slider 9 to drive the stator 6 to rotate or move, and when the stator 6 rotates or moves Change the eccentricity to change the displacement.
  • This configuration is advantageous for reducing power consumption, reducing power consumption, and increasing the power usage of the fluid medium within the variable feedback chamber 14.
  • the slider 9 does not operate, and only when the pressure of the variable feedback chamber 14 reaches the set pressure, the slider 9 overcomes the elastic force of the variable spring 5 to cause the eccentricity of the stator 6 to occur. Variety.
  • a plurality of blades 10 are respectively engaged with the grooves or gaps 7.1 of the rotor 7, and the blades 10 are located in the stator 6, and the stator 6 is located in the slider 9. Therefore, in operation, the inner surface of the stator 6 is subjected to the action of the vane 10 to generate an internal torque. The outer surface of the stator 6 is subjected to the action of the slider 9, creating an external torque. The internal torque and the external torque act on the stator 6, respectively, which causes the stator 6 to produce three operating states. It is easy to understand that in the three operating states of the T surface, when the pressure of the variable feedback chamber 14 reaches the set pressure, the slider 9 overcomes the elastic force of the variable spring 5 to change the eccentricity of the stator 6.
  • the first operational state is that, in the case where the internal torque is small and the external torque is large, the internal torque is insufficient to overcome the external torque, and the stator 6 does not rotate due to the external torque.
  • the oil pump in this case is no different from the general vane pump.
  • the second operational state is: in the case where the internal torque is greater than the external torque so as to provide sufficient driving force, at this time, driven by the internal torque, the blade 10 abuts against the inner surface of the stator 6, so that the stator 6 and the blade 10 And the rotor 7 rotates at the same speed, the running speed of this is relatively fast, and the stator 6 is rotated at a high speed with respect to the slider 9.
  • the main friction and relative motion exist between the stator 6 and the slider 9, which is similar to the principle of the prior rotor pump.
  • the third operational state is: In the case where the internal torque is equivalent to the external torque, the state is between the first and second operational states.
  • the stator 6 rotates, but there is insufficient driving force, and only the rotor 7 and the n-plate 10 rotate at the same speed, and the stator 6 forms a differential rotation with the rotor 7 and the blade 10.
  • the stator 6 operates at a lower speed than the blades 10.
  • This third operating state is a typical operating state, achieving a good balance between energy consumption and operational reliability. That is, it can reduce energy consumption, and the reliability of the oil pump is better.
  • the present invention can realize three operating states by separately producing and processing the integrally connected stator 6 and the slider 9, and this operating state can be applied to the inside of the stator 6 according to actual operation.
  • the relationship between the internal torque of the surfaces and the external torque is switched to achieve a better balance between reducing energy consumption, reducing friction and achieving better reliability. This can further improve the performance of the oil pump of the internal combustion engine and prolong the use of the oil pump of the internal combustion engine. Life expectancy.

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

Abstract

一种内燃机的机油泵包括：转子组件（2）；叶片组件（3），该叶片组件与转子组件连接；以及定子组件（4），该定子组件包括定子（6）和滑块（9），该定子套接在滑块内；当叶片组件与转子组件同步旋转时，定子和滑块可相对转动。这种机油泵能够根据实际工况来改善运转状况，从而减少能耗和改善摩擦状况。

Description

內燃机的机油荥
技术领域
本发明涉及内燃机润滑系统技术领域， 具体涉及一种内燃机的机油泵。 背景技术
随着对燃油经济性的日渐重视以及发动机新技术的应用，对用亍内燃机的润滑系统提出了 越来越高的要求。例如， 现有技术中通过变排量的方式来降低发动机的燃油消耗、 改善润滑性 能已经成为一种普遍的技术趋势。而变排量的叶片泵因其变排量的方式简单可靠、总效率高而 被广泛的应用于内燃机的润滑， 从而出现了用于内燃机的可变排量叶片式机油泵。现有技术的 叶片式机油泵主要包括泵体、泵盖、定子、转子和控制机构，其结构和原理与现有叶片泵类似。 但由于该用于内燃机的机油泵并未在结构上改进， 其运转模式与普通的叶片泵基本没有差异， 导致不能根据实际工况来改变运转模式， 从而使得其能耗和摩擦得不到改善。 发明内容
本发明所要解决的技术问题是， 提供一种内燃机的机油泵， 其能根据实际工况来改善运转 状况从而减少能耗和改善摩擦状况。
本发明的技术解决方案是， 提供一种具有以下结构的内燃机的机油泵， 包括； 转子组件； 叶片组件， 其与转子组件连接； 和
定子组件，包括定子和滑块，所述定子套接在滑块内；当叶片组件与转子组件同步转动 ^1% 所述定子和滑块可相对转动。
与现有技术相比，本发明的内燃机的机油泵具有以下有益效果。 由于叶片组件与转子组件 基本是同歩转动， 定子和滑块可相对转动， 这样定子的运转模式可分为定子不转动、 定子与叶 片同速转动而定子相对滑块转动以及第三种是定子与 n†片差速转动。 因此，根据实工况来选择 其中一种运转模式， 例如， 在内部扭短和外部扭矩相差不多的情况下， 定子与叶片差速运转。 由于在这种情况下， 定子可以运动， 因此会减少定子的表面以及叶片的磨损， 从而保证了泵的 性能和可靠性。 另外， 定子转动， 会减少定子与叶片之间以及定子与滑块之间的摩擦。 由于叶 片是通过发动机等来驱动的， 因此改善摩擦状况的同时也减少了能耗。
在一个实施例中， 所述定子为圆环结构， 所述滑块与定子同心且间隙配合。 现有技术中的 定子承载了本发明中的定子和滑块 S者的功能， 为不规则形状， 对其进行特殊工艺处理或者采 ^特定材质加工时， 增加了加工的难度， 也极大地增加了成本。本发明中的定子为相对比较规 则的圆环结构， 因此， 方便对定子表面进行特殊的工艺处理和 Z或采用特殊的材质进行制作。 例如采用钢件来制作定子， 或者采用淬火等工艺来提高定子的表靣质量。 因此， 本发明的定子 既能达到更好的效果， 例如耐磨性更好， 更不容易损坏等。 同时又能降低加工难度， 极大地降 低加工成本。
在一个优选的实施例中， 所述滑块和定子采用不同的材料和表面处理工艺， 所述滑块和定 子可相对高速转动。根据滑块和定子的用途和工作需要来对滑块和定子进行处理，有利于降低 成本， 同时又能提高滑块和定子的使用寿命。
在一个实施例中， 所述叶片组件包括两端的定位环和若千叶片， 所述叶片径向连接在两个 定位环的外周面上且向定子组件的方向延伸。通过 S定位环来连接和固定叶片， 可减少整个叶 片组件的重量。
在一个实施例中， 所述转子组件包括驱动轴和转子， 所述转子上均布有容纳 ^片的凹槽或 间隙； 优选地， 所述转子组件由电机或曲轴直接驱动。 当然， 转子组件也可以被间接驱动。
在一个实施例中， 所述机油泵的泵体内还包括设在滑块外的矩形密封条， 所述矩形密封条 与滑块的旋转定位弧面形成封闭的变量反馈腔。 由于定子的偏心会发生变化，通过矩形密封条 能形成更好的密封。
在一个实施例中， 当变量反馈腔的压力达到调定压力时， 滑块克服连接在其上的变量弹性 件的弹性力从而带动定子转动或移动从而改变排量。该特征不仅适用于单腔反馈， 而且对变量 反馈腔中的流体介质没有限制， 既可以是油液， 也可以是水或其它流体。
在一个实施例中， 在内部扭矩小、 外部扭矩大的情况下， 定子不转动。 外部扭矩明显大于 内部扭矩时， 内部扭矩不足以克服外部扭矩的作用， 定子不转动。这种情况与普通的叶片泵基 本相同。
在一个实施例中， 在内部扭矩大于外部扭矩从而能够提供驱动力的情况下， 定子与叶片同 速转动， 定子相对滑块高速转动。这种情况是内部扭矩明显大于外部扭矩， 在克服外部扭矩的 基础上还能够提供驱动力来驱动定子转动。此时定子和叶片之间由于作用力和反作用力的作用 下而同速转动。受到的阻力和摩擦力主要存在与定子的外表面与滑块之间。 由于叶片一直牢固 顶在定子的内表面上， 不容易出现磨损和泄漏， 因此， 该机油泵能可靠地进行工作。
在一个实施例中， 在内部扭矩与外部扭矩的大小相当的情况下， 定子、 转子和叶片差速转 动。这种情况是内部扭矩与外部扭矩相差不多或基本相等的情况。这种情况介于定子不转动和 定子与叶片同速转动这两种情况之间。 能耗较少， 同时摩擦也不大， 因此是一种比较理想的运 转状态。 另外， 由亍叶片与定子之间的作用力和摩擦力均比较小， 又处于相互接触的状态， 使 得工作时的可靠性较高。 附圏说明
图 1所示是本发明的内燃机的机油泵未安装泵盖时的结构示意图。
图 2所示是图 1中的部分零部件的拆分结构示意图。 具体实施方式
下面结合附图和具体实施例对本发明作进一歩说明。
如图 1所示为本发明的内燃机的机油泵一种具体实施例。其中图 1示出的是该内燃机的机 油泵在未安装泵盖时的内部结构示意简图。 该内燃机的机油泵主要包括泵体 、 转子组件 2、 叶片组件 3、 定子组件 4以及泵盖 （未示出） 。 其中， 主动轴转子组件 2、 叶片组件 3和定子 组件 4均设在泵体 1的腔体内。泵体 1和泵盖密封后通过紧固件连接。转子组件 2由电机或曲 轴直接驱动。
由于现有技术中的定子需要兼具滑块的功能， 因此其结构比较复杂， 复杂的定子结构使得 要提高定子表靣质量需要特别的处理方式， ί到如蒸汽处理。但即便如此， 现有技术中的定子的 表面质量的提升受到限制， 例如蒸汽处理得到的处理层很薄， 在工作时容易被快速磨损从而影 响机油泵的性能。 另外， 叶片出现卡滞^ , 由于定子的外部结构复杂， 会导致摩擦阻力很大， 从而损坏定子表面， 导致机油泵失效。而在本发明的实施例中， 定子组件 4主要包括圆环状的 定子 6和不规则形状的滑块 9。 定子 6套接在滑块 9内。 定子 6与滑块 9为间隙配合。 这种结 构相当于将现有技术中的兼具滑块的功能特征的定子分成了定子 6和滑块 9两部分。因此， 当 叶片组件 3与转子组件 2同歩转动时， 定子 6和滑块 9可相对转动。优选地， 对滑块 9和定子 6采用不同的村料和表面处理工艺，即能提高滑块 9和定子 6的性能，又能尽可能地降低成本。
在一个实施例中， 转子组件 2主要包括主动轴 13和转子 7。 其中主动轴 13和转子 7可以 做成一体， 也可以做成两部分然后进行装配。 主动轴 13与电机的输出轴或曲轴直接连接从而 构成电机或曲轴直接驱动转子组件 2。 优选地， 转子 7的外表靣设有若干凹槽或间隙 7.1。
在一个实施例中， 叶片组件 3主要包括两端的定位环 8和若干 n†片 10。 叶片 10径向连接 在两个定位环 8的外周面上。 在轴向方向上， 叶片 10的两端稍凸出两端的定位环 8。 在径向 方向上， 叶片 10向定子 6的方向延伸。 装配时， 若干个叶片】0分别配合在在运动 叶片 10径向抵接在定子 6的内表面。
在一个实施例中，本发明的内燃机的机油泵的泵体 1 内还包括设在滑块 9外的矩形密封条 11。 矩形密封条 1 与橡胶棒 12—起使用。 矩形密封条 11与滑块 9的旋转定位弧面形成封闭 的变量反馈腔 14。 优选地， 当变量反馈腔 14的压力达到调定压力时， 滑块 9克服作用在该滑 块 9的外表面的变量弹簧 5的弹性力从而带动定子 6转动或移动，定子 6转动或移动时改变偏 心状况从而改变排量。 这种结构有利于降低功率消耗， 降低能耗， 提高变量反馈腔 14内的流 体介质的功率使用率。
在本发明的实施例中， 一般情况下滑块 9不动作， 仅当变量反馈腔 14的压力达到调定压 力时， 滑块 9才克服变量弹簧 5的弹性力作用而使定子 6的偏心发生变化。
本发明的内燃机的机油泵装配完成后， 若干个叶片 10分别对应卡接在转子 7的凹槽或间 隙 7.1上， 叶片 10位于定子 6内， 定子 6位于滑块 9内。 因此， 工作时， 定子 6的内表面受 到叶片 10的作用， 产生一个内部扭矩。 定子 6的外表面受到滑块 9的作用， 产生一个外部扭 矩。 内部扭矩和外部扭矩分别作用在定子 6上， 会使定子 6产生三种运转状态。 容易理解地， 在 T面三种运转状态中均会出现： 当变量反馈腔 14的压力达到调定压力时， 滑块 9克服变量 弹簧 5的弹性力作^而使定子 6的偏心发生变化。
第一种运转状态是：在内部扭矩小、夕卜部扭矩大的情况下， 内部扭矩不足以克服外部扭矩， 由于受到外部扭矩的作用，定子 6不发生转动。这种情况下的机油泵跟一般的叶片泵没有差异。
第二种运转状态是： 在内部扭矩大于外部扭矩从而能够提供足够的驱动力的情况下，此时 在内部扭矩的驱动下， 叶片 10抵接在定子 6的内表面， 使得定子 6与 片 10以及转子 7同速 转动， 此^的运转速度相对较快， 定子 6相对滑块 9是高速转动。主要的摩擦和相对运动存在 于定子 6与滑块 9之间， 这与现有转子泵的原理类似。
第三种运转状态是： 在内部扭矩与外部扭矩的大小相当的情况下， 这种状态是位于第一种 和第二种运转状态之间。 定子 6会转动， 但没有足够的驱动力， 仅转子 7和 n†片 10同速转动， 而定子 6与转子 7以及叶片 10之间形成了差速转动。 定子 6以低于叶片 10的转速进行运转。 这第三种运转状态是比较典型的运转状态， 在能耗和运转可靠性之间达到了一种比较好的平 衡。 即既能降低能耗， 同^该机油泵的可靠性又比较好。
在本发明的实施例中， 由于定子 6与滑块 10之间的间隙配合， 以及可旋转的定子 6, 能 够有效克服曲轴传动 曲轴或转子组件振动传递的叶片振动对定子表面的破坏性影响，显著改 善可变排量叶片式机油泵的可靠性， 特别是曲轴直接驱动式机油泵。
因此，本发明通过将一体连接的定子 6和滑块 9分开进行生产和加工后， 能够实现_三种运 转状态，而旦这 种运转状态可根据实际运转时作用在定子 6的内夕卜两个表面的内部扭矩以及 外部扭矩之间的关系来进行切换， 从而在降低能耗、减少摩擦和达到较好的可靠性之间达到一 个比较好的平衡。这也进一步能提高该内燃机的机油泵的性能， 延长该内燃机的机油泵的使用 寿命。
虽然已经结合具体实施例对本发明进行了描述， 然而可以理解， 在不脱离本发明的范圏的 情况下， 可以对其进行各种改进或替换。 尤其是， 只要不存在结构上的冲突， 各实施例中的特 征均可相互结合起来， 所形成的组合式特 ¾E仍属于本发明的范围内。本发明并不局限于文中公 开的特定实施例， 而是包括落入权利要求的范围内的所有技术方案。

Claims

权利要求书
1 . 一种内燃机的机油泵， 包括：
转子组件；
叶片组件， 其与转子组件连接； 和
定子组件，包括定子和滑块，所述定子套接在滑块内；当叶片组件与转子组件同步转动 ^1% 所述定子和滑块 相对转动。
2. 根据权利要求 1所述的内燃机的机油泵， 其特征在于， 所述定子为圆环结构， 所述滑 块与定子同心且间隙配合。
3. 根据权利要求 1或 2所述的内燃机的机油泵， 其特征在于， 所述滑块和定子采用不同 的材料和表面处理工艺， 所述定子可相对滑块高速转动。
4. 根据权利要求 1〜3中任一项所述的内燃机的机油泵， 其特征在于， 所述叶片组件包括 两端的定位环和若千†片，所述叶片径向连接在两个定位环的夕卜周面上且向定子组件的方向延 伸。
5. 根据权利要求 1〜4中任一项所述的内燃机的机油泵， 其特征在于， 所述转子组件包括 驱动轴和转子， 所述转子上均布有容纳叶片的凹槽或间隙； 优选地， 所述转子组件由电机或曲 轴直接驱动。
6. 根据权利要求 1〜5中径一项所述的内燃机的机油泵， 其特征在于， 所述机油泵的泵体 内还包括设在滑块外的矩形密封条，所述矩形密封条与滑块的旋转定位弧面形成封闭的变量反 馈腔。
7. 根据权利要求 6所述的内燃机的机油泵， 其特征在于， 当变量反馈腔的压力达到调定 压力时， 滑块克服连接在其上的变量弹性件的弹性力从而带动定子转动或移动丛而改变排量。
8. 根据权利要求 1〜7中任一项所述的内燃机的机油泵， 其特 ¾E在于， 在内部扭矩小、 外 部扭矩大的情况下， 定子不转动。
9. 根据权利要求 1〜8中任一项所述的内燃机的机油泵， 其特 ¾E在于， 在内部扭矩大亍外 部扭矩从而能够提供驱动力的情况下， 定子与叶片同速转动， 定子相对滑块高速转动。
10. 根据权利要求 1〜9中任一项所述的内懲机的机油泵， 其特征在于， 在内部扭矩与外部 扭矩的大小相当的情况下， 定子、 转子和叶片差速转动。
PCT/CN2014/084743 2014-08-19 2014-08-19 内燃机的机油泵 WO2016026091A1 (zh)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111237625A (zh) * 2020-04-08 2020-06-05 湖南机油泵股份有限公司 一种防卡滞高效率的变速器油泵

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007012096A2 (de) * 2005-07-29 2007-02-01 Miba Sinter Holding Gmbh & Co Kg Flügelzellenpumpe
JP2010223110A (ja) * 2009-03-24 2010-10-07 Hitachi Automotive Systems Ltd 可変容量形ベーンポンプ
CN103097731A (zh) * 2010-03-25 2013-05-08 欧瑞康纺织有限及两合公司 齿轮泵
CN203477846U (zh) * 2013-07-28 2014-03-12 湖南机油泵股份有限公司 机械阀控制的双腔变排量叶片式机油泵的主体泵

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007012096A2 (de) * 2005-07-29 2007-02-01 Miba Sinter Holding Gmbh & Co Kg Flügelzellenpumpe
JP2010223110A (ja) * 2009-03-24 2010-10-07 Hitachi Automotive Systems Ltd 可変容量形ベーンポンプ
CN103097731A (zh) * 2010-03-25 2013-05-08 欧瑞康纺织有限及两合公司 齿轮泵
CN203477846U (zh) * 2013-07-28 2014-03-12 湖南机油泵股份有限公司 机械阀控制的双腔变排量叶片式机油泵的主体泵

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111237625A (zh) * 2020-04-08 2020-06-05 湖南机油泵股份有限公司 一种防卡滞高效率的变速器油泵
CN111237625B (zh) * 2020-04-08 2024-04-16 湖南机油泵股份有限公司 一种防卡滞高效率的变速器油泵

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