WO2013010320A1 - Pompe hydraulique variable et procédé de commande de sa cylindrée - Google Patents

Pompe hydraulique variable et procédé de commande de sa cylindrée Download PDF

Info

Publication number
WO2013010320A1
WO2013010320A1 PCT/CN2011/077330 CN2011077330W WO2013010320A1 WO 2013010320 A1 WO2013010320 A1 WO 2013010320A1 CN 2011077330 W CN2011077330 W CN 2011077330W WO 2013010320 A1 WO2013010320 A1 WO 2013010320A1
Authority
WO
WIPO (PCT)
Prior art keywords
servo
hydraulic variable
rotary valve
electromagnetic solenoid
swash plate
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.)
Ceased
Application number
PCT/CN2011/077330
Other languages
English (en)
Chinese (zh)
Inventor
程宇
王晶
帕特森查德
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.)
Sauer Shanghai Hydrostatic Transmission Co Ltd
Original Assignee
Sauer Shanghai Hydrostatic Transmission Co Ltd
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 Sauer Shanghai Hydrostatic Transmission Co Ltd filed Critical Sauer Shanghai Hydrostatic Transmission Co Ltd
Priority to CN201180071411.4A priority Critical patent/CN104136775B/zh
Priority to PCT/CN2011/077330 priority patent/WO2013010320A1/fr
Publication of WO2013010320A1 publication Critical patent/WO2013010320A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block

Definitions

  • the invention relates to the technical field of hydraulic transmission, in particular to a hydraulic variable pump and a displacement control method thereof. Background technique
  • the hydraulic pump and the hydraulic motor constitute an energy conversion device in the hydraulic system.
  • the former converts the mechanical energy of the prime mover into the hydraulic energy of the liquid; the latter converts the hydraulic energy into a mechanical energy output to perform the required action.
  • the hydraulic motor is a hydraulic actuator that achieves continuous rotary motion.
  • variable displacement hydraulic pump can output different flows at the same speed as required. This type of pump is called a variable pump.
  • the traditional hydraulic variable pump's electric proportional displacement control (EDC) and / or forward / neutral / reverse three-position control (FNR) use two linear electrical devices or servo valve type devices to drive displacement control.
  • a hydraulic variable pump having a swash plate and a servo piston coupled to the swash plate, the swash plate adjusting an inclination angle thereof by movement of the servo piston And thereby changing the displacement of the hydraulic variable pump
  • the hydraulic variable pump further comprising: an electromagnetic servo valve that converts the input electrical signal into a hydraulic signal and outputs a flow rate to the servo piston, and further a servo piston that tilts the swash plate;
  • the electromagnetic servo valve is composed of a rotating electromagnetic solenoid and a servo rotary valve, and an output shaft of the rotary electromagnetic solenoid is linked with a spool of a servo rotary valve, when Rotating the output of the electromagnetic solenoid When the shaft rotates, the spool of the servo rotary valve is excited to rotate.
  • the rotating electromagnetic solenoid is a rotating bi-directional proportional electromagnetic solenoid for performing electrical proportional displacement control of the hydraulic variable pump in both forward and reverse directions.
  • the hydraulic variable pump further includes an angle feedback mechanism
  • the servo rotary valve further includes a valve sleeve
  • the valve sleeve is rotated relative to a sleeve fixed in a casing of the hydraulic variable pump
  • the angle feedback mechanism is connected Valve sleeve and swashplate.
  • the angle feedback mechanism senses an offset of the swash plate from a preset position, and excites the servo rotary valve according to the offset and controls movement of the servo piston by flow to keep the swash plate at Its predetermined setting position.
  • the servo rotary valve is coupled to the swash plate by the angle feedback mechanism when performing electrical proportional displacement control.
  • the servo rotary valve has a return spring, and the return spring performs an automatic returning function and a proportional control function of the spool of the servo rotary valve when the input signal is missing.
  • the rotating electromagnetic solenoid is a rotary two-way electromagnetic solenoid for three-position control of forward/neutral/reverse of the hydraulic variable pump.
  • the servo rotary valve and the swash plate are not connected by a feedback mechanism.
  • the servo rotary valve has a return spring, and the return spring performs an automatic returning function of the spool of the servo rotary valve when the input signal is missing.
  • the swash plate is coupled to the servo piston by a slider.
  • the servo rotary valve is a spring-returned 3-position 4-way servo rotary valve.
  • the hydraulic variable pump is an axial piston variable pump.
  • the output shaft of the rotary electromagnetic solenoid and the valve core of the servo rotary valve are directly fixedly connected.
  • the spool and the valve sleeve of the servo rotary valve are sealed by a seal ring and an O-ring.
  • Another object of the present invention is to provide a technical solution for performing electrical proportional displacement control of a hydraulic variable pump using a rotating bi-directional proportional electromagnetic solenoid.
  • a method of performing electrical proportional displacement control using a hydraulic variable pump wherein the rotating electromagnetic solenoid is a rotating two-way proportional electric power a magnetic solenoid, the servo rotary valve is a spring-returned servo rotary valve, and the method comprises the following steps:
  • the output shaft of the rotating bi-directional proportional electromagnetic solenoid generates a positive angle-torque output proportional to the control current signal upon receiving a positive control current signal;
  • An angle-torque output of an output shaft of the rotating bi-directional proportional electromagnetic solenoid, a rotational angle of the rotating bi-directional proportional electromagnetic solenoid and the spool, and a servo to the servo when a reverse control current signal is input The output flow of the piston will also be reversed, whereby the movement of the servo piston will also be reversed, causing the swash plate to tilt proportionally in the negative direction, thereby achieving negative displacement control of the hydraulic variable pump.
  • the hydraulic variable pump further includes an angle feedback mechanism, wherein the servo rotary valve is connected to the swash plate through the angle feedback mechanism, and the angle feedback mechanism senses an offset of the swash plate from a preset position. Exciting the servo rotary valve according to the offset and controlling the movement of the servo piston by the flow rate to maintain the swash plate at its predetermined set position.
  • a method of performing forward/neutral/reverse three-position control using a hydraulic variable pump according to the above, wherein the rotary electromagnetic solenoid is a rotary two-way electromagnetic solenoid, the method Includes the following steps:
  • the output shaft of the rotating bi-directional electromagnetic solenoid Upon receiving a positive electrical input signal, the output shaft of the rotating bi-directional electromagnetic solenoid produces a positive maximum angle-torque output;
  • the servo rotary valve outputs a positive maximum flow to the servo piston to make the servo piston position Move to the positive maximum position;
  • the servo piston tilts the swash plate to a forward maximum position to achieve a positive maximum displacement of the hydraulic variable pump
  • the servo rotary valve and the swash plate are not connected by a feedback mechanism.
  • the present invention creatively proposes a new concept of integrated rotary electromagnetic servo for hydraulic variable displacement pump control.
  • the use of a rotating electromagnetic solenoid and a servo rotary valve for displacement control of the hydraulic variable pump greatly simplifies the operation of the EDC and FNR controls.
  • the present invention makes it easier to design hardware compatible with the mechanical displacement control.
  • the device of the present invention is compact in size and achieves the same function while reducing the number and complexity of parts, and is therefore less susceptible to part tolerances.
  • FIG. 1 is a perspective view of a hydraulic variable pump in accordance with an embodiment of the present invention.
  • Figure 2 is a front elevational view of the hydraulic variable pump of Figure 1;
  • Figure 3A is a cross-sectional view taken along line A-A of Figure 2.
  • Fig. 3B is a cross-sectional view taken along line B-B in Fig. 2. detailed description
  • the hydraulic variable pump is an axial piston variable pump.
  • the hydraulic variable pump of the present invention may also be a swash plate type axial piston pump or a slant shaft type shaft. Pump to the plunger, etc.
  • the swash plate type axial piston pump has a swash plate 10 and a servo piston 12 connected to the swash plate 10, and the swash plate .10 adjusts the inclination angle thereof by the movement of the servo piston 12, thereby changing the position The displacement of the swash plate type axial piston pump.
  • the swash plate type plunger pump further includes: an electromagnetic servo valve 20 that converts an input electrical signal into a hydraulic signal and outputs a flow rate to the servo piston 12, and the servo piston 12 causes the slant The disk 10 is tilted.
  • the electromagnetic servo valve 20 is composed of a rotary electromagnetic solenoid 1 and a servo rotary valve 15, and the servo rotary valve 15 is composed of a spool 2 of a servo rotary valve and a valve sleeve 3 of a servo rotary valve, and the rotary electromagnetic
  • the output shaft of the solenoid 1 is interlocked with the spool 2 of the servo rotary valve, and when the output shaft of the rotary electromagnetic solenoid 1 is rotated, the spool 2 of the servo rotary valve is excited to rotate.
  • the swash plate type axial piston pump includes a casing 13, a valve sleeve 3 of the servo rotary valve is moved relative to the sleeve 4, and the sleeve 4 is fixed to the outer casing 13.
  • An angle feedback mechanism (such as a feedback link) 5 connects the valve sleeve 3 of the servo rotary valve and the swash plate 10.
  • the swash plate 10 is connected to the servo piston 12 in the servo cylinder 11 via the slider 9.
  • the servo piston 12 is positioned in the servo cylinder 11 by a servo spring 8.
  • the rotating electromagnetic solenoid 1 is a rotating bidirectional proportional electromagnetic solenoid.
  • the rotating bi-directional proportional electromagnetic solenoid 1 receives the control current signal, it has an angle-torque output proportional to the control current signal. Since the spool 2 of the servo rotary valve is directly fixedly coupled to the output shaft of the rotary bidirectional proportional electromagnetic solenoid 1, it rotates together with the output shaft of the rotary bidirectional proportional electromagnetic solenoid 1. The rotation of the spool 2 of the servo rotary valve opens the hydraulic port of the valve sleeve 3 of the servo rotary valve.
  • the spool 2 of the servo rotary valve and the valve sleeve 3 of the servo rotary valve are the same. It is a 3-position 4-way servo rotary valve that constitutes a spring return.
  • the 3-position 4-way servo rotary valve includes a return spring or a return torsion spring (not shown) that interacts with the spool 2.
  • the return spring is used to realize the automatic return function and proportional control function of the spool 2 in the absence of the input control current signal during EDC control.
  • control current signal is converted into a hydraulic pressure signal by the spring-returned 3-position 4-way servo rotary valve 15, and the flow rate is output to the two sides of the servo piston 12 through the 3-position 4-way servo rotary valve 15, and the servo piston is caused by the pressure. 12 linear motion.
  • the servo piston 12 tilts the swash plate 10 by the slider 9, thereby changing the displacement of the hydraulic variable pump from the neutral position to the forward position.
  • the swash plate 10 is easily offset from a preset position.
  • the offset sensed by the feedback link 5 energizes the 3-position 4-way servo rotary valve 15 and supplies flow to the servo piston 12 to maintain the swash plate 10 in its forward, predetermined position.
  • the rotary proportional electromagnetic solenoid 1 provides the output flow to the servo piston 12 through the spool 2 of the servo rotary valve, the torque generated by the spring force and the input torque signal can be generated by the action of the three-position four-way servo-turned return spring. Proportional to achieve proportional displacement control.
  • the larger input signal causes a greater spring torque, and in turn corresponds to the larger angle of rotation of the servo spool 2, then increasing the input signal will increase the input flow to the servo piston 12 and change the angle of the swash plate 10, Until the maximum displacement is achieved.
  • the rotating electromagnetic solenoid 1 It is selected to rotate the two-way electromagnetic solenoid, and the swash plate 10 is not connected to the valve sleeve 3 of the servo rotary valve 15 through the feedback link 5.
  • the other structure of the swash plate type axial piston pump is the same as that of the above-described swash plate type axial piston pump when performing EDC control.
  • the rotating bidirectional electromagnetic solenoid 1 When the rotating bidirectional electromagnetic solenoid 1 receives an electrical input signal, it produces a positive maximum angle - torque output. Since the spool 2 of the servo rotary valve is directly connected to the output shaft of the rotary bidirectional electromagnetic solenoid 1, it rotates to the positive maximum angle together with the output shaft of the rotary bidirectional electromagnetic solenoid 1. Therefore, since the operating electric input signal of the spring-returned 3-position 4-way servo rotary valve 15 is converted into the hydraulic pressure signal, the 3-position 4-way servo rotary valve 15 outputs the maximum hydraulic flow to both sides of the two-way acting servo piston 12 due to The pressure difference across the servo piston 12 is maximized, causing the servo piston 12 to shift to the positive maximum position.
  • the servo piston 12 tilts the swash plate 10 to the forward maximum position by the slider 9, so that the hydraulic variable pump (i.e., the swash plate type axial piston pump) achieves a positive maximum displacement.
  • the input signal reversely input to the rotary bidirectional electromagnetic solenoid 1 can achieve the negative maximum displacement of the swash plate type axial piston pump.
  • the input signal is removed. Due to the action of the return spring of the servo rotary valve 15, the pressure on both sides of the servo piston 12 is equal, and the swash plate 10 is reset to the neutral position, which will realize the neutral position of the pump.
  • the return spring of the servo rotary valve 15 can perform the automatic returning function of the spool 2 of the servo rotary valve 15 when the electric input signal is omitted. Therefore, the FNR control of the hydraulic variable pump can be realized by the rotary two-way electromagnetic solenoid 1.
  • the servo rotary valve 15 may not be provided with a return spring, and in this case, the corresponding input signal can be used to reset the swash plate 10 to the neutral position, thereby The hydraulic variable pump is in the neutral position.
  • the EDC or FNR control of the hydraulic variable pump can be easily realized by applying the rotary electromagnetic solenoid 1 and the servo rotary valve 15.
  • the one rotating electromagnetic solenoid of the present invention can replace two linear electrical devices or servo valve type devices in the prior art. Therefore, the EDC, FNR operations are greatly simplified.
  • the present invention makes it easier to design hardware compatible with mechanical displacement control, and the device of the present invention is compact, and achieves the same function while reducing the number and complexity of parts. It is also less affected by part tolerances. While some embodiments of the present general inventive concept have been shown and described, it will be understood by those of ordinary skill in the art that the present invention may be modified without departing from the principles and spirit of the present general inventive concept. The scope is defined by the claims and their equivalents.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe hydraulique variable comprenant un plateau cyclique (10) et un piston (12) d'asservissement relié au plateau cyclique. Le plateau cyclique règle son angle d'inclinaison par un mouvement du piston d'asservissement, de façon à modifier la cylindrée de la pompe hydraulique variable. La pompe hydraulique variable comporte en outre une servo-vanne électromagnétique (20). La servo-vanne électromagnétique convertit un signal électrique d'entrée en signal hydraulique et envoie un débit vers le piston d'asservissement ; le piston d'asservissement incline alors le plateau cyclique. La servo-vanne électromagnétique est formée d'un solénoïde électromagnétique rotatif (1) et d'une servo-vanne rotative (15). Une transmission est formée entre un arbre de sortie du solénoïde électromagnétique rotatif et un tiroir cylindrique (2) de la servo-vanne rotative. Lorsque l'arbre de sortie du solénoïde électromagnétique rotatif tourne, le tiroir cylindrique de la servo-vanne rotative est entraîné en rotation. L'invention concerne également un procédé utilisant la pompe hydraulique variable pour réaliser une commande électrique de cylindrée et une commande de type marche avant / point mort / marche arrière.
PCT/CN2011/077330 2011-07-19 2011-07-19 Pompe hydraulique variable et procédé de commande de sa cylindrée Ceased WO2013010320A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201180071411.4A CN104136775B (zh) 2011-07-19 2011-07-19 液压变量泵及其排量控制方法
PCT/CN2011/077330 WO2013010320A1 (fr) 2011-07-19 2011-07-19 Pompe hydraulique variable et procédé de commande de sa cylindrée

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2011/077330 WO2013010320A1 (fr) 2011-07-19 2011-07-19 Pompe hydraulique variable et procédé de commande de sa cylindrée

Publications (1)

Publication Number Publication Date
WO2013010320A1 true WO2013010320A1 (fr) 2013-01-24

Family

ID=47557644

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2011/077330 Ceased WO2013010320A1 (fr) 2011-07-19 2011-07-19 Pompe hydraulique variable et procédé de commande de sa cylindrée

Country Status (2)

Country Link
CN (1) CN104136775B (fr)
WO (1) WO2013010320A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104533740A (zh) * 2014-12-30 2015-04-22 南京萨伯工业设计研究院有限公司 伺服变量斜盘柱塞泵及其控制方法
CN104533741A (zh) * 2014-12-30 2015-04-22 南京萨伯工业设计研究院有限公司 伺服控制变量柱塞泵及其控制方法
CN107209510A (zh) * 2014-12-08 2017-09-26 罗伯特·博世有限公司 用于识别特性曲线的方法

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020210397B3 (de) * 2020-08-14 2021-10-14 Danfoss Power Solutions Gmbh & Co. Ohg Hydrostatische servoeinheit

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6463665A (en) * 1987-09-02 1989-03-09 Tokyo Keiki Kk Control device for variable displacement pump
CN2244627Y (zh) * 1995-06-05 1997-01-08 上海科曼电气公司 数字液压泵的变量控制机构
JP2000297743A (ja) * 1999-04-09 2000-10-24 Kayaba Ind Co Ltd ポンプ制御装置
US20020176784A1 (en) * 2001-05-16 2002-11-28 Hongliu Du Method and apparatus for controlling a variable displacement hydraulic pump
CN1392345A (zh) * 2001-06-18 2003-01-22 尤尼西亚Jkc控制系统株式会社 用于动力转向装置的变量泵的控制装置
CN201202622Y (zh) * 2008-04-03 2009-03-04 中山市钜通机电技术有限公司 一种比例变量柱塞泵
JP2010168974A (ja) * 2009-01-21 2010-08-05 Toshiba Mach Co Ltd 建設機械
CN101956686A (zh) * 2010-10-21 2011-01-26 吴赛珍 一种位置-弹簧-力反馈式电比例变量轴向柱塞泵

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6463665A (en) * 1987-09-02 1989-03-09 Tokyo Keiki Kk Control device for variable displacement pump
CN2244627Y (zh) * 1995-06-05 1997-01-08 上海科曼电气公司 数字液压泵的变量控制机构
JP2000297743A (ja) * 1999-04-09 2000-10-24 Kayaba Ind Co Ltd ポンプ制御装置
US20020176784A1 (en) * 2001-05-16 2002-11-28 Hongliu Du Method and apparatus for controlling a variable displacement hydraulic pump
CN1392345A (zh) * 2001-06-18 2003-01-22 尤尼西亚Jkc控制系统株式会社 用于动力转向装置的变量泵的控制装置
CN201202622Y (zh) * 2008-04-03 2009-03-04 中山市钜通机电技术有限公司 一种比例变量柱塞泵
JP2010168974A (ja) * 2009-01-21 2010-08-05 Toshiba Mach Co Ltd 建設機械
CN101956686A (zh) * 2010-10-21 2011-01-26 吴赛珍 一种位置-弹簧-力反馈式电比例变量轴向柱塞泵

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107209510A (zh) * 2014-12-08 2017-09-26 罗伯特·博世有限公司 用于识别特性曲线的方法
CN104533740A (zh) * 2014-12-30 2015-04-22 南京萨伯工业设计研究院有限公司 伺服变量斜盘柱塞泵及其控制方法
CN104533741A (zh) * 2014-12-30 2015-04-22 南京萨伯工业设计研究院有限公司 伺服控制变量柱塞泵及其控制方法

Also Published As

Publication number Publication date
CN104136775B (zh) 2016-10-12
CN104136775A (zh) 2014-11-05

Similar Documents

Publication Publication Date Title
CN105134578A (zh) 一种具备能量回收功能的柱塞泵
CN104136775B (zh) 液压变量泵及其排量控制方法
JP3877307B2 (ja) 圧油エネルギー回収装置
CN103697000A (zh) 实现执行机构无级变速的液压控制系统
CN204984843U (zh) 具备能量回收功能的柱塞泵
WO2015078421A1 (fr) Système de direction à télécommande pour véhicule et véhicule en étant doté
CN203604291U (zh) 实现执行机构无级变速的液压控制系统
CN108533545B (zh) 液压变量泵机械比例控制器及液压变量泵
JPH02195062A (ja) 機械油圧式伝動装置とその制御方法
JP2014196726A (ja) 対向式斜板型ピストンポンプ・モータ
JP2008057687A (ja) 油圧制御装置
CN109592585B (zh) 起重机回转制动系统及起重机
KR101259912B1 (ko) 유압식 동력 전달장치의 가변용량형 유압펌프 제어용 서보밸브 제어장치
JP2010105636A (ja) 油圧駆動車両
CN111720377A (zh) 一种功率控制阀块、液压泵组件及工程机械
CN107131277B (zh) 基于压力控制的机液复合传动系统
CN108679018A (zh) 一种回转式电液驱动器及控制方法
JP2014190434A (ja) 作業機
CN117799692B (zh) 一种变排量闭式液压直驱回路的铰接车辆动力转向系统
WO2006025519A1 (fr) Dispositif d’entraînement hydraulique et procédé de changement de vitesses dans un dispositif d’entraînement hydraulique
CN119687053B (zh) 一种凸轮变量泵控制系统
JPH0533776A (ja) 可変容量型油圧ポンプの容量制御装置
CN223823338U (zh) 基于四轮原地转向系统的高空作业平台
JPS5916483Y2 (ja) エア−モ−タ−の電気制御装置
US12247374B2 (en) Working machine

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11869577

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 11869577

Country of ref document: EP

Kind code of ref document: A1