WO2014047769A1 - 一种作用面积可变的往复式低速重载液压泵 - Google Patents

一种作用面积可变的往复式低速重载液压泵 Download PDF

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Publication number
WO2014047769A1
WO2014047769A1 PCT/CN2012/081886 CN2012081886W WO2014047769A1 WO 2014047769 A1 WO2014047769 A1 WO 2014047769A1 CN 2012081886 W CN2012081886 W CN 2012081886W WO 2014047769 A1 WO2014047769 A1 WO 2014047769A1
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WO
WIPO (PCT)
Prior art keywords
hydraulic cylinder
hydraulic pump
hydraulic
reversing valve
speed heavy
Prior art date
Application number
PCT/CN2012/081886
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English (en)
French (fr)
Inventor
孙威
Original Assignee
Sun Wei
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
Priority to PCT/CN2012/081886 priority Critical patent/WO2014047769A1/zh
Application filed by Sun Wei filed Critical Sun Wei
Priority to DK12885646.5T priority patent/DK2902628T3/en
Priority to ES12885646.5T priority patent/ES2671936T3/es
Priority to NZ707315A priority patent/NZ707315B2/en
Priority to US14/430,748 priority patent/US10280917B2/en
Priority to NO12885646A priority patent/NO2902628T3/no
Priority to JP2015532267A priority patent/JP6138945B2/ja
Priority to PT128856465T priority patent/PT2902628T/pt
Priority to AU2012391449A priority patent/AU2012391449B2/en
Priority to CN201280076161.8A priority patent/CN104968940A/zh
Priority to EP12885646.5A priority patent/EP2902628B1/en
Publication of WO2014047769A1 publication Critical patent/WO2014047769A1/zh
Priority to ZA2015/02843A priority patent/ZA201502843B/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/18—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the effective cross-section of the working surface of the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
    • F03G7/08—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for recovering energy derived from swinging, rolling, pitching or like movements, e.g. from the vibrations of a machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F04B49/246—Bypassing by keeping open the outlet valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B5/00—Machines or pumps with differential-surface pistons
    • F04B5/02—Machines or pumps with differential-surface pistons with double-acting pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical

Definitions

  • the invention belongs to an oil pump, in particular to a reciprocating low speed heavy duty hydraulic pump with variable action area.
  • One of the typical types of pumps is a positive displacement pump. It relies on the periodic variation of the volume of the sealed working space containing the liquid to periodically transfer energy to the liquid. The pressure of the liquid increases, and then the liquid is forced. discharge. The amount of discharge fluid flow depends on the volume change of the sealed chamber.
  • the two necessary conditions for the operation of the positive displacement pump are: 1) There is a periodic change in the sealing volume, the sealing volume is sucked from small to large, and the oil is changed from large to small; 2) There is an oil distribution device for ensuring the sealing volume When it becomes small, it only communicates with the oil suction pipe, and it only communicates with the pressure oil pipe from large change to small.
  • the technical problem to be solved by the present invention is to provide a reciprocating low-speed heavy-duty hydraulic pump with a variable working area for working conditions of reciprocating driving and low running speed.
  • Reciprocating low-speed heavy-duty hydraulic pump with variable action area including several groups of hydraulic cylinders
  • the unit (3), the moving part (1) and the moving part (2) are characterized in that both ends of the hydraulic cylinder unit (3) are respectively connected to the moving part (1) and the moving part (2) by a mechanical mechanism, and the moving part ( 1)
  • the valve (5) and the check valve (6) are connected by a hydraulic line.
  • the reversing valve (5) adopts a two-position two-way electromagnetic reversing valve (5'), and the port B is unidirectionally cut off to the port A.
  • the reversing valve (5) adopts a two-position two-way electromagnetic reversing valve (5"), and the port A and the port B are bidirectionally cut off.
  • the hydraulic cylinder (4) employs a single rod piston cylinder (4').
  • the hydraulic cylinder (4) employs a plunger cylinder (4").
  • the hydraulic cylinder (4) uses a double-outlet piston cylinder (4"').
  • the device can form a combination of different hydraulic cylinder units by actively setting according to the magnitude of the driving force, thereby achieving the adjustment of the equivalent effective working area. In this way, even if the magnitude of the driving force is changed, the corresponding hydraulic pump is changed by setting.
  • the size of the effect area ensures that the hydraulic pump composed of the hydraulic cylinder unit outputs a relatively stable pressure oil for use in the after-sale system.
  • the reciprocating low-speed heavy-duty hydraulic pump with variable action area has the advantages of high conversion efficiency, simple system structure and good working stability.
  • Figure 2 is a schematic diagram of the system principle of the hydraulic cylinder unit (3)
  • FIG. 3 is a schematic diagram of the system principle of the first embodiment of the hydraulic cylinder unit (3)
  • Figure 4 is a schematic diagram of the system principle of the second embodiment of the hydraulic cylinder unit (3)
  • Figure 5 is a schematic diagram of the system principle of the third embodiment of the hydraulic cylinder unit (3)
  • a reciprocating low-speed heavy-duty hydraulic pump with variable action area comprises a plurality of hydraulic cylinder units (3), a moving part (1) and a moving part (2), characterized by a hydraulic cylinder unit (3) Both ends are mechanically coupled to the moving part (1) and the moving part (2) Connected, there is relative movement between the moving part (1) and the moving part (2), and the hydraulic cylinder unit (3) consists of a hydraulic cylinder (4), a reversing valve (5) and a check valve (6) The hydraulic cylinder (4), the reversing valve (5) and the check valve (6) are connected by a hydraulic line.
  • the working principle is as follows: Under the action of external force, the relative displacement between the moving part (1) and the moving part (2) is generated, the hydraulic cylinder unit (3) is retracted and moved, and the oil is sucked through the port D, through the port C. Confluent output pressure oil.
  • the hydraulic pump output can be relatively stable by setting the working combination of hydraulic cylinder units (3) of different numbers or different sizes.
  • the hydraulic cylinder unit (3) consists of a hydraulic cylinder (4), a reversing valve (5) and a check valve (6), between the hydraulic cylinder (4), the reversing valve (5) and the check valve (6).
  • the hydraulic line Connected by the hydraulic line, when the reversing valve (5) is in the control position, the port A and the port B are connected, and when in the non-control position, the port A and the port B are not connected.
  • the working principle is: When the reversing valve (5) is in the non-control position, the port A and the port B are not connected, and when the hydraulic cylinder (4) is retracting, the hydraulic cylinder (4) passes through the check valve (6) The pressure oil is output from the port C, and at the same time, the hydraulic cylinder (4) sucks the oil from the port D; when the hydraulic cylinder (4) is extended, the oil is output from the port D and passes through the reversing valve (5) ) To the port C, input the hydraulic cylinder (4). If the input hydraulic pressure is insufficient, the hydraulic cylinder (4) will suck the oil from the hydraulic oil tank (5) through the reversing valve (6) to the port C.
  • the check valve (6) is mainly used to ensure that the pressure oil output from the hydraulic cylinder unit (3) flows to the same place without mutual interference. See Figure 3. It is a schematic diagram of the system principle of the first embodiment of the hydraulic cylinder unit (3).
  • the hydraulic cylinder unit (3) is mainly composed of a single rod piston cylinder (4'), a two-position two-way electromagnetic reversing valve (5') and a one-way valve (6).
  • the working process is as follows: When the two-position two-way electromagnetic reversing valve (5') is not energized, the two-position two-way electromagnetic reversing valve (5') works in the right position, and the port B is directed to the port A. One-way cutoff.
  • the single rod piston cylinder (4') also draws in oil from the port D through the 2/2-way electromagnetic reversing valve (5').
  • the two-position two-way electromagnetic reversing valve (5') When the two-position two-way electromagnetic reversing valve (5') is energized, the two-position two-way electromagnetic reversing valve (5') works in the left position, the port A and the port B are connected, and the single rod piston cylinder
  • the rod chamber of (4') is connected to the rodless chamber and is connected to the port D.
  • the single rod piston cylinder (4') is freely telescopic and does not generate any pressure oil.
  • the hydraulic cylinder unit (3) is mainly composed of a plunger cylinder (4"), a 2/2-way electromagnetic reversing valve (5'), and a check valve (6).
  • the working process is as follows: When the two-position two-way electromagnetic reversing valve (5') is not energized, the two-position two-way electromagnetic reversing valve (5') works in the right position, and the port B is directed to the port A. One-way cutoff. When the plunger cylinder (4") is retracted, the plunger cylinder (4") is passed through the check valve (6) Port C outputs pressure oil; when the plunger cylinder (4") is extended, the plunger cylinder (4") draws oil from port D through the 2/2-way solenoid reversing valve (5'). liquid.
  • the two-position two-way electromagnetic reversing valve (5') When the two-position two-way electromagnetic reversing valve (5') is energized, the two-position two-way electromagnetic reversing valve (5') works in the left position, the port A and the port B are connected, and the plunger cylinder (4) ") Connected to port D. At this time, the plunger cylinder (4") is free to expand and contract, and no pressure oil is generated.
  • the hydraulic cylinder unit (3) is mainly composed of a double-outlet piston cylinder (4"'), a two-position two-way electromagnetic reversing valve (5"), and a one-way valve (6).
  • the working process is as follows: When the two-position two-way electromagnetic reversing valve (5") electromagnet is not energized, the two-position two-way electromagnetic reversing valve (5") works in the right position, at this time, port A and port B Two-way deadline.
  • the double-outlet piston cylinder (4"') When the double-outlet piston cylinder (4"') is actuated downward, the double-outlet piston cylinder (4"') lower chamber passes the check valve (6) to output the pressure oil from the port C, the double-outlet piston The upper chamber of the cylinder (4"') draws oil from port D via the check valve (6); when the double rod piston cylinder (4"') moves upward, the double rod piston cylinder (4"' The lower chamber draws oil from port D via a check valve (6), and the upper chamber of the double rod piston cylinder (4"') outputs pressure oil from port C via a check valve (6).
  • the two-position two-way electromagnetic reversing valve (5") electromagnet When the two-position two-way electromagnetic reversing valve (5") electromagnet is energized, the two-position two-way electromagnetic reversing valve (5") works in the left position, the oil port A and the oil port B are connected, and the double-out rod piston cylinder The upper and lower chambers of the (4"') are connected to the port D via the check valve (6). At this time, the double-outlet piston cylinder (4"') is freely telescopic and does not generate any pressure oil. If oil leakage loss occurs during free expansion, the oil will be replenished from port D via check valve (6).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

一种作用面积可变的往复式低速重载液压泵，包括若干组液压缸单元（3）和运动部件（1，2），液压缸单元（3）两端通过机械结构分别与运动部件（1，2）相连接，运动部件（1，2）之间存在相对运动，液压缸单元（3）由液压缸（4）、换向阀（5）以及单向阀（6）组成，液压缸（4）、换向阀（5）以及单向阀（6）之间均由液压管路相连接。该液压泵能够根据驱动作用力的大小不同，通过主动设置形成不同液压缸单元的组合，进而实现调节等效作用面积的大小。如此，便能实现即使驱动作用力大小在变化，也能够确保由液压缸单元组成的液压泵输出压力相对稳定的压力油液，供后接***使用。该作用面积可变的往复式低速重载液压泵具有转化效率高、***结构简单、工作稳定性好等优点。

Description

说 明 书 一种作用面积可变的往复式低速重载液压泵 技术领域
本发明属于一种油泵，具体涉及一种作用面积可变的往复式低速 重载液压泵。
背景技术
液压泵的种类繁多， 其典型类型代表之一是容积式泵， 它依靠包 容液体的密封工作空间容积的周期性变化，把能量周期性地传递给液 体， 是液体的压力增加， 然后将液体强行排出。 其排出油液流量的大 小取决于密封腔的容积变化。 容积式泵工作的两个必要条件是： 1 ) 有周期性的密封容积变化， 密封容积由小变大时吸油， 由大变小时压 油； 2 )有配油装置， 用于保证密封容积由小变大时只与吸油管连通， 由大变小时只与压油管连通。
然而传统的容积式泵通常需要旋转转速较高的原动机来驱动，然 而在往复式驱动且运行速度较低的情况下，传统的容积式泵无法应用 于此类情况中。
发明内容
本发明所要解决的技术问题是：针对往复式驱动且运行速度较低 的工作条件下， 提供一种作用面积可变的往复式低速重载液压泵。
本发明可通过下列技术方案来实现：
一种作用面积可变的往复式低速重载液压泵，包括若干组液压缸 单元 （3)， 运动部件 （1) 和运动部件 （2)， 其特征在于液压缸单元 (3) 两端通过机械机构分别与运动部件 （1) 和运动部件 （2) 相连 接， 运动部件（1)和运动部件（2)之间存在相对运动， 液压缸单元 (3) 由液压缸（4)、换向阀（5)以及单向阀（6)组成， 液压缸（4)、 换向阀 （5) 以及单向阀 （6) 之间均由液压管路相连接。
所述换向阀 （5) 处于控制位时， 油口 A和油口 B连通， 处于非 控制位时， 油口 A和油口 B不连通。
所述换向阀 （5) 采用二位二通电磁换向阀 （5')， 且油口 B向油 口 A单向截止。
所述换向阀 （5)采用二位二通电磁换向阀 （5")， 且油口 A和油 口 B双向截止。
所述液压缸 （4) 采用单出杆活塞缸 （4')。
所述液压缸 （4) 采用柱塞缸 （4")。
所述液压缸 （4) 采用双出杆活塞缸 （4"')。
这种作用面积可变的往复式低速重载液压泵工作时，通过切换换 向阀 （5) 的不同控制位功能， 从而控制换向阀 （5)所对应控制的液 压缸单元（3)是否参与泵送油液。当参与泵送油液的液压缸单元（3) 数量减少时， 该液压泵的等效作用面积将减少； 当参与泵送油液的液 压缸单元 （3) 数量增多时， 该液压泵的等效作用面积将增大。
本装置能够根据驱动作用力的大小不同，通过主动设置形成不同 液压缸单元的组合， 进而实现调节等效作用面积的大小。 如此， 便能 实现即使驱动作用力大小在变化，但是通过设置改变液压泵相应的等 效作用面积大小，就能够确保由液压缸单元组成的液压泵输出压力相 对稳定的压力油液， 供后接***使用。该作用面积可变的往复式低速 重载液压泵具有转化效率高、 ***结构简单、 工作稳定性好等优点。
往复式低速重载液压泵的后续***中，通常有液压蓄能器类的元 器件， 用于稳定压力。 如果作用面积不可变， 则很难做到动力源的出 力与蓄能器压力之间的匹配， 即动力源出力小的时候， 液压泵输出压 力无法超过蓄能器， 液压泵动不了； 而动力源输出力过大时， 使液压 泵可以输出的压力远超蓄能器压力， 造成运行速度过快等问题， 是一 种浪费。 因此， 如果液压泵的作用面积可变， 使得动力源输出力、 液 压泵输出压力、与蓄能器所维持的***压力相匹配， 才能够充分利用 动力源的交变动力。
附图说明
图 1是本发明的原理示意图。
图 2是液压缸单元 （3 ) 的***原理示意图
图 3是液压缸单元 （3 ) 实施例一的***原理示意图
图 4是液压缸单元 （3 ) 实施例二的***原理示意图
图 5是液压缸单元 （3 ) 实施例三的***原理示意图 具体实施方案
参见图 1， 一种作用面积可变的往复式低速重载液压泵， 包括若 干组液压缸单元 （3 )， 运动部件 （1 ) 和运动部件 （2 )， 其特征在于 液压缸单元（3 )两端通过机械机构分别与运动部件（1 )和运动部件 (2) 相连接， 运动部件 （1) 和运动部件 （2) 之间存在相对运动， 液压缸单元 （3) 由液压缸 （4)、 换向阀 （5) 以及单向阀 （6) 组成， 液压缸（4)、换向阀（5) 以及单向阀（6)之间均由液压管路相连接。
其工作原理是： 在外力的作用下， 运动部件（1)和运动部件（2) 之间产生相对位移， 液压缸单元 （3) 做来回伸缩动作， 并通过油口 D吸油， 通过油口 C合流输出压力油液。 根据外力大小的不同， 可通 过设置不同数量或不同面积大小的液压缸单元 （3) 的工作组合， 来 实现液压泵输出相对稳定的压力油液。
参见图 2， 液压缸单元（3) 的***原理示意图。 液压缸单元（3) 由液压缸 （4)、 换向阀 （5) 以及单向阀 （6) 组成， 液压缸 （4)、 换 向阀（5)以及单向阀（6)之间均由液压管路相连接，所述换向阀（5) 处于控制位时， 油口 A和油口 B连通， 处于非控制位时， 油口 A和油 口 B不连通。
其工作原理是： 当换向阀 （5) 处于非控制位时， 油口 A和油口 B 不连通， 液压缸 （4) 作缩进动作时， 液压缸 （4) 经单向阀 （6) 从油口 C输出压力油液， 同时， 液压缸 （4) 从油口 D吸入油液； 液 压缸（4)作伸出动作时， 从油口 D输出油液并经换向阀 （5)到油口 C, 输入液压缸（4)， 若输入液压流量不足时， 液压缸（4)从液压油 箱 （5) 经换向阀 （6) 至油口 C, 吸入油液。 当换向阀 （5) 处于控 制位时， 油口 A和油口 B连通， 液压缸 （4) 作自由伸缩动作， 不产 生任何压力油液。 单向阀 （6)主要用于确保液压缸单元（3)输出的 压力油液均流向同一处， 而不会发生相互干扰。 参见图 3。 是液压缸单元 （3) 实施例一的***原理示意图。 液 压缸单元（3)主要由单出杆活塞缸（4')、、二位二通电磁换向阀（5') 以及单向阀 （6) 组成。
其工作过程是： 当二位二通电磁换向阀 （5') 电磁铁不得电时， 二位二通电磁换向阀 （5') 工作在右位， 此时油口 B向油口 A单向截 止。 当单出杆活塞缸 （4') 作缩进动作时， 单出杆活塞缸 （4') 的无 杆腔经单向阀 （6) 从油口 C输出压力油液， 单出杆活塞缸 （4') 的 有杆腔从油口 D吸入油液； 当单出杆活塞缸 （4') 作伸出动作时， 单 出杆活塞缸 （4') 的有杆腔输出油液并经二位二通电磁换向阀 （5') 输入单出杆活塞缸 （4') 的无杆腔， 由于无杆腔和有杆腔作用面积不 同， 会出现单出杆活塞缸 （4') 无杆腔的容积变化要大于有杆腔， 因 此， 单出杆活塞缸 （4') 还会从油口 D, 经二位二通电磁换向阀 （5') 吸入油液。 当二位二通电磁换向阀 （5') 电磁铁得电时， 二位二通电 磁换向阀（5')工作在左位，油口 A和油口 B连通，单出杆活塞缸（4') 的有杆腔与无杆腔相连通， 且均与油口 D相连通， 此时， 单出杆活塞 缸 （4') 作自由伸缩动作， 不产生任何压力油液。
参见图 4。 是液压缸单元 （3) 实施例二的***原理示意图。 液 压缸单元（3)主要由柱塞缸（4")、、 二位二通电磁换向阀 （5') 以及 单向阀 （6) 组成。
其工作过程是： 当二位二通电磁换向阀 （5') 电磁铁不得电时， 二位二通电磁换向阀 （5') 工作在右位， 此时油口 B向油口 A单向截 止。 当柱塞缸 （4") 作缩进动作时， 柱塞缸 （4") 经单向阀 （6) 从 油口 C输出压力油液； 当柱塞缸 （4") 作伸出动作时， 柱塞缸 （4") 会从油口 D, 经二位二通电磁换向阀 （5') 吸入油液。 当二位二通电 磁换向阀 （5') 电磁铁得电时， 二位二通电磁换向阀 （5') 工作在左 位， 油口 A和油口 B连通， 柱塞缸 （4") 与油口 D相连通， 此时， 柱 塞缸 （4") 作自由伸缩动作， 不产生任何压力油液。
参见图 5。 是液压缸单元 （3) 实施例三的***原理示意图。 液 压缸单元（3)主要由双出杆活塞缸（4"')、二位二通电磁换向阀（5") 以及单向阀 （6) 组成。
其工作过程是： 当二位二通电磁换向阀 （5") 电磁铁不得电时， 二位二通电磁换向阀 （5")工作在右位， 此时油口 A和油口 B双向截 止。 当双出杆活塞缸 （4"') 作向下动作时， 双出杆活塞缸 （4"') 下 腔体经单向阀 （6) 从油口 C输出压力油液， 双出杆活塞缸 （4"') 的 上腔体经单向阀 （6) 从油口 D吸入油液； 当双出杆活塞缸 （4"') 作 向上动作时， 双出杆活塞缸 （4"') 的下腔体经单向阀 （6) 从油口 D 吸入油液， 双出杆活塞缸 （4"') 的上腔体经单向阀 （6) 从油口 C输 出压力油液。 当二位二通电磁换向阀 （5") 电磁铁得电时， 二位二通 电磁换向阀 （5")工作在左位， 油口 A和油口 B连通， 双出杆活塞缸 (4"') 的上、 下腔体均经单向阀 （6) 与油口 D相连通， 此时， 双出 杆活塞缸（4"')作自由伸缩动作， 不产生任何压力油液， 如自由伸缩 过程中出现油液泄漏损失， 油液将经单向阀 （6) 从油口 D处补充进

Claims

权 利 要 求 书
1、 一种作用面积可变的往复式低速重载液压泵，包括若干组液压 缸单元 （3)， 运动部件 （1) 和运动部件 （2)， 其特征在于液压缸单 元 （3) 两端通过机械机构分别与运动部件 （1) 和运动部件 （2) 相 连接， 运动部件 （1)和运动部件（2) 之间存在相对运动， 液压缸单 元 （3) 由液压缸 （4)、 换向阀 （5) 以及单向阀 （6) 组成， 液压缸
(4)、 换向阀 （5) 以及单向阀 （6) 之间均由液压管路相连接。
2、 根据权利要求 1 所述的一种作用面积可变的往复式低速重载 液压泵， 其特征在于： 所述换向阀 （5) 处于控制位时， 油口 A和油 口 B连通， 处于非控制位时， 油口 A和油口 B不连通。
3、 根据权利要求 2 所述的一种作用面积可变的往复式低速重载 液压泵，其特征在于：所述换向阀（5)采用二位二通电磁换向阀（5' )， 且油口 B向油口 A单向截止。
4、 根据权利要求 2 所述的一种作用面积可变的往复式低速重载 液压泵，其特征在于：所述换向阀（5)采用二位二通电磁换向阀（5")， 且油口 A和油口 B双向截止。
5、 根据权利要求 1或 2所述的一种作用面积可变的往复式低速重 载液压泵， 其特征在于： 所述液压缸 （4) 采用单出杆活塞缸 （4')。
6、 根据权利要求 1或 2所述的一种作用面积可变的往复式低速重 载液压泵， 其特征在于： 所述液压缸 （4) 采用柱塞缸 （4")。
7、 根据权利要求 1或 2所述的一种作用面积可变的往复式低速重 载液压泵， 其特征在于： 所述液压缸 （4) 采用双出杆活塞缸 （4"')。
PCT/CN2012/081886 2012-09-25 2012-09-25 一种作用面积可变的往复式低速重载液压泵 WO2014047769A1 (zh)

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