WO2012024945A1 - Soupape de suspension, système de suspension hydropneumatique et véhicule d'ingénierie - Google Patents

Soupape de suspension, système de suspension hydropneumatique et véhicule d'ingénierie Download PDF

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Publication number
WO2012024945A1
WO2012024945A1 PCT/CN2011/074254 CN2011074254W WO2012024945A1 WO 2012024945 A1 WO2012024945 A1 WO 2012024945A1 CN 2011074254 W CN2011074254 W CN 2011074254W WO 2012024945 A1 WO2012024945 A1 WO 2012024945A1
Authority
WO
WIPO (PCT)
Prior art keywords
suspension
valve
oil
interface
differential pressure
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/CN2011/074254
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English (en)
Chinese (zh)
Inventor
詹纯新
刘权
李英智
张建军
郭堃
李义
郭纪梅
胡廷江
王启涛
刘学检
冯科喜
奉松生
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.)
Hunan Zoomlion Special Vehicle Co Ltd
Changsha Zoomlion Heavy Industry Science and Technology Development Co Ltd
Original Assignee
Hunan Zoomlion Special Vehicle Co Ltd
Changsha Zoomlion Heavy Industry Science and Technology Development 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 Hunan Zoomlion Special Vehicle Co Ltd, Changsha Zoomlion Heavy Industry Science and Technology Development Co Ltd filed Critical Hunan Zoomlion Special Vehicle Co Ltd
Publication of WO2012024945A1 publication Critical patent/WO2012024945A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
    • B60G17/056—Regulating distributors or valves for hydropneumatic systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
    • B60G17/052—Pneumatic spring characteristics

Definitions

  • the invention relates to a suspension valve. Furthermore, the invention relates to an oil and gas suspension system and an engineering vehicle comprising the suspension valve. Background technique
  • Hydro-pneumatic suspension systems are widely used in a variety of mobile construction machinery, such as wheel loaders, mine dump trucks, wheeled excavators, and mobile cranes.
  • the existing oil and gas suspension system is mainly realized by a combination of a suspension cylinder and an accumulator, a suspension cylinder and an accumulator plus a suspension valve combination.
  • Each manufacturer basically adopts a suspension cylinder and an accumulator plus a suspension valve combination.
  • each of the axles A is symmetrically disposed with suspension cylinders 7, 10, the upper ends of the suspension cylinders 7, 10 are hinged to the frame F or the body, and the lower ends are hinged to the corresponding axles A.
  • Each pair of suspension cylinders 7, 10 is connected with a matching suspension valve 8, 9 and an accumulator 4, and the existing suspension technology, such as the patent CN 101618669A, uses a two-position two-way valve to control the same side suspension cylinder.
  • the rod cavity is connected with the accumulator to realize the rigid and flexible conversion of the suspension system.
  • the so-called rigid state means that the suspension cylinder is only subjected to the weight of the whole vehicle by a certain rod cavity, and the cylinder has a rod cavity and a damping component.
  • the accumulator is connected, and the flexible state is reversed; the rigid state is generally used when the vehicle is hoisting (such as a mobile crane lifting heavy objects) and the vehicle is completely extinguished and broken, and the rest of the working conditions generally use a flexible state. .
  • each suspension cylinder communicates with the accumulator on the opposite side thereof to obtain a large roll stiffness, and the pressure oil passage and the return oil passage are respectively controlled by the 2/2-way valve and the rodless cavity of the suspension cylinder respectively.
  • the connection between the two to achieve the lifting control of the vehicle body, the oil and gas suspension circuit of the middle axle and the rear axle oil and gas suspension control loop is a lifting control group to realize the leveling operation of the vehicle body, which is essentially through the suspension valve Suspension cylinders and accumulators are connected to this universal mode for suspension.
  • the existing hydro-pneumatic suspension technology adopts a two-position two-way valve for rigid flexible conversion, which is affected by the suspension cylinder, and the suspension system cannot be effectively locked in a rigid state, in a flexible state.
  • the two-position two-way valve directly bears the vehicle pressure, because the hydraulic pressure and the air pressure of the two-position two-way valve are relatively large, and there is a possibility that the flexibility is automatically converted into rigidity when the pressure of the air pressure changes.
  • the suspension valve preferentially causes the suspension to rise, resulting in a complicated logic relationship of the suspension valve, and the number of hydraulic components used for the lifting function must be increased, which also increases the difficulty of logic control.
  • the technical problem to be solved by the present invention is to provide a suspension valve which can ensure the stability of the flexible working condition and realize the main functions of the suspension valve, and has the advantages of strong control capability, simple control logic relationship and reliable operation.
  • the invention also provides an oil and gas suspension system, which can ensure stable and flexible working conditions, has strong control capability, simple control logic relationship and reliable operation.
  • the present invention also provides an engineering vehicle, wherein the oil and gas suspension system of the engineering vehicle can ensure stable and flexible working conditions, has strong control capability, simple control logic relationship, and reliable operation.
  • the present invention provides a suspension valve, wherein the suspension valve includes: an oil inlet switch lock valve, the oil inlet switch lock valve is connected to the oil inlet and the second interface of the suspension valve a return oil switch lock valve, the oil return switch lock valve is connected between the oil return port of the suspension valve and the first interface; a differential pressure sensing logic control component group, the differential pressure sensing logic control component The group includes a logic shuttle valve, a differential pressure sensing lock valve, and a pilot control valve, wherein the oil inlet of the logic shuttle valve is respectively connected to the first interface and the accumulator interface of the suspension valve, the energy storage
  • the device interface is connected to the second interface via a side chamber of the differential pressure sensing lock valve, and a side chamber of the differential pressure sensing lock valve is further connected to the first interface, When the differential pressure sensing lock valve is locked, the accumulator interface is disconnected from the first interface oil passage, and the differential pressure sensing lock valve is another a side chamber connected to an oil outlet of the logic shuttle valve and
  • the present invention also provides an oil and gas suspension system, wherein the oil and gas suspension system includes at least one pair of the above suspension valves, and the at least one pair of suspension valves are respectively connected with a matching left suspension cylinder group and a right suspension cylinder group
  • the rod cavities of the left suspension cylinders of the left suspension cylinder group are in communication with each other, and the rodless cavities of the respective left suspension cylinders are also in communication with each other, in the right suspension cylinder group
  • the rod cavities of the respective right suspension cylinders are in communication with each other, and the rodless cavities of the respective right side suspension cylinders are also in communication with each other, wherein the first interface of the left suspension valve of the pair of suspension valves is opposite to the left side a rodless cavity of each of the left suspension cylinders in the suspension cylinder group is connected, and a second interface is connected to a rod cavity of each right suspension cylinder in the right suspension cylinder group, the pair of suspension valves
  • the first interface of the right side suspension valve is in communication with the rodless
  • the present invention provides an engineering vehicle including the above-described oil and gas suspension system.
  • the invention realizes the priority lifting function of the axle suspension system through effective oil circuit design; the rigid flexible working condition of the suspension system is more reliably realized by using the differential pressure sensing logic control component group. Long-term maintenance and reliable and fast conversion of rigid flexible working conditions; At the same time, various components of the suspension valve of the axle suspension system are effectively reduced, and the problems of complicated control, complicated logic relationship, etc. caused by the prior art are avoided, and the suspension system is improved. The simplicity of control. Other features and advantages of the invention will be described in detail in the detailed description which follows. DRAWINGS The drawings are intended to provide a further understanding of the invention, and are intended to be a In the drawing:
  • FIG. 1 is a schematic structural view of a prior art oil and gas suspension system
  • FIG. 2 is a schematic view showing the principle of a suspension valve according to an embodiment of the present invention.
  • Figure 3 is a schematic diagram of a conventional installation of a suspension valve applied to an oil and gas suspension system
  • FIG. 4 is a schematic view of a novel connection structure of a suspension valve according to an embodiment of the present invention.
  • Fig. 5 is a schematic view showing a grouping arrangement structure of an oil and gas suspension system according to an embodiment of the present invention. Description of the reference signs:
  • A1 first interface A2 second interface
  • orientation words used for clarity and convenience such as the front left side, the front right side, the rear left side, and the rear right side, are all the same as the actual installation of the oil and gas suspension system to the construction vehicle. It is not intended to limit the scope of the invention.
  • Fig. 1 shows a general installation form of a suspension valve in an oil and gas suspension system, in which each side of the axle A is symmetrically provided with suspension cylinders 7, 10, and the upper ends of the suspension cylinders 7, 10 are hinged. On the frame F or the body, the lower end is hinged to the corresponding axle A, and each pair of suspension cylinders 7, 10 is connected with a matching suspension valve 8, 9 and an accumulator 4, 5.
  • the suspension valve comprising: an oil inlet switch lock valve 22 connected to an oil inlet P and a second interface A2 of the suspension valve Between the second interface A2 for connecting the rod cavity of the suspension cylinder; the oil return switch lock valve 21, the oil return switch lock valve 21 is connected to the return port T of the suspension valve and the first interface A1 Between the first interface A1 for connecting the rodless cavity of the suspension cylinder; the differential pressure sensing logic control component group, the differential pressure sensing logic control component group comprises a logic shuttle valve 23 and a differential pressure sensing locking valve 24 And a pilot control valve 25, wherein the oil outlet of the logic shuttle valve 23 is connected to the first interface A1 and the accumulator interface SP of the suspension valve, respectively, the accumulator interface SP via the differential pressure sensing lock valve 24 One side chamber is connected to the second interface A2, and one side chamber of the differential pressure sensing lock valve 24 is also connected to the first interface Al, when the differential pressure sensing lock valve 24 is locked, the accumulator interface SP
  • the oil return switch lock valve 21 adopts an electronically controlled electromagnetic valve to realize the oil return opening and locking function
  • the oil inlet switch lock valve 22 adopts an electronically controlled electromagnetic valve to realize the oil inlet opening and locking function
  • the logic shuttle valve 23 is suspended.
  • the pressure cylinder has a pressure logic comparison of the rod cavity
  • the differential pressure sensing lock valve 24 realizes the pressure difference pressure sensing and the communication lock of the suspension cylinder with or without the rod cavity
  • the pilot control valve 25 realizes whether the suspension cylinder has a rod cavity Connectivity and locking.
  • the logic shuttle valve 23, the differential pressure sensing lock valve 24, and the pilot control valve 25 form a differential pressure sensing logic control element group.
  • the pilot control valve 25 is a pneumatic pilot control valve, and the control interface X of the suspension valve is connected to a source of pressurized gas.
  • FIG. 3 shows a conventional installation form of the suspension valve of the present invention.
  • the suspension system of FIG. 3 includes an oil source 1, a PLC or a microcomputer control unit 2, a fuel tank 3, and an accumulator 4, 5, 15, 17.
  • each pair of suspension cylinders (for example, a front left suspension cylinder 7 and a front right suspension cylinder 10; and a rear left suspension cylinder 13 and The rear right suspension cylinder 18) is provided with a pair of suspension valves, wherein the cross-connection relationship is well known, and the corresponding control logic relationship is also well known to those skilled in the art, and will not be described again, mainly by various work.
  • the PLC or the microcomputer control unit 2 controls the suspension valve and the oil path to realize the extension and retraction of the vehicle suspension cylinder or the leveling position locking, thereby satisfying various suspension requirements of the vehicle.
  • Fig. 4 shows a mounting form of a renewed type hydro-pneumatic suspension system using the suspension valve of the present invention (the above-described interface connection relationship of the known cross-installation type can also be referred to the mounting form).
  • the oil and gas suspension system includes at least one pair of the above suspension valves, the at least one pair of suspensions
  • the valve is connected with a matching left suspension cylinder group and a right suspension cylinder group, wherein the left suspension cylinders of the left suspension cylinder group have a rod cavity communicating with each other, and each left suspension
  • the rodless chambers of the cylinders 7 are also in communication with each other, and the rod cavities of the respective right side suspension cylinders 10 in the right side suspension cylinder group are in communication with each other, and the rodless chambers of the respective right side suspension cylinders 10 are also in communication with each other.
  • the first interface A1 of the left suspension valve 8 of the pair of suspension valves is in communication with the rodless cavity of each of the left suspension cylinders 7 in the left suspension cylinder group
  • the second interface A2 is a rod cavity of each of the right suspension cylinders 10 in the right suspension cylinder group, a first interface A1 of the right suspension valve of the pair of suspension valves and each of the right suspension cylinder groups
  • the rodless chamber of the side suspension cylinder 10 is in communication
  • the second port A2 is in communication with the rod chamber of each of the left suspension cylinders 7 in the left suspension cylinder group, the left side suspension valve and the right side suspension valve
  • the accumulator interfaces SP are connected to the left accumulator 5 and the right accumulator 4, respectively.
  • the first port A1 of the suspension valve is connected to the rodless cavity of the suspension cylinder
  • the second port A2 is connected to the rod cavity of the suspension cylinder
  • the accumulator port SP is connected to the accumulator
  • P is the oil inlet
  • T For the return port
  • the control interface X is connected to the pneumatic control air supply.
  • control interface X is connected to the source of pressurized air by an electrically controlled pneumatic valve 20.
  • the T port oil returns to the suspension port through the oil return switch lock valve 21 and the first port A1.
  • the rodless cavity achieves the priority retraction function of the suspension cylinder, which realizes the priority lifting function of the axle suspension system.
  • the control interface X turns on the pressure air source, so that the pilot control valve 25 connects the control port of the differential pressure sensing lock valve 24 to the fuel tank 3
  • the presence or absence of the rod cavity pressure of the suspension cylinder simultaneously pushes the differential pressure sensing lock valve 24 to communicate with the rod cylinder, the rodless chamber and the accumulator of the suspension cylinder, and can stably and directly suspend when the air pressure changes.
  • the hydro-pneumatic suspension system since it includes the left suspension cylinder group and the right suspension cylinder group, the grouping of the front and rear suspension cylinders of the vehicle can be realized according to the position of the center of gravity of the vehicle.
  • FIG. 5 a grouping arrangement of an oil and gas suspension system of a five-axle vehicle according to a position of a center of gravity of a vehicle is shown, wherein a vehicle center of gravity position G (ie, a centroid position of the vehicle) is located between the front bridge group FG and the rear bridge group BG,
  • the bridge group FG comprises two axles
  • the rear axle group BG comprises three axles, that is to say, the number of axles of the rear axle group BG is one more than the number of axles of the front axle group FG.
  • the upper end of the suspension cylinder of the oil and gas suspension system is hinged on the frame or the vehicle body, and the lower end is hinged on the corresponding axle ( That is, the suspension cylinders are symmetrically arranged on both sides of each axle, wherein the axle includes a front axle group FG and a rear axle group BG, and the center of gravity position G of the vehicle is located in the front bridge group FG and the rear bridge group Between the BGs, and the number of axles of the rear axle group BG is equal to the number of axles of the front axle group FG, or only one axle more than the number of axles of the front axle group FG.
  • the corresponding front left suspension cylinder group and front right suspension cylinder group can be installed by using a pair of suspension valves as shown in FIG. 4, similarly,
  • the rear left suspension cylinder group and the rear right suspension cylinder group can also be mounted using a pair of suspension valves as shown in FIG. That is to say, the function is realized as described with reference to Fig. 4, which simultaneously realizes the control of the rigid flexible switching function of the suspension system, and the object of control changes from a single suspension cylinder to a group suspension cylinder.
  • the present invention realizes the priority lifting function of the axle suspension system through effective oil circuit design; and realizes the long-term maintenance of the rigid flexible working condition of the suspension system by using the differential pressure sensing logic control component group more reliably.
  • Reliable and fast conversion of rigid flexible working conditions effectively reducing various components of the suspension valve of the axle suspension system, avoiding the complicated control and logical relationship caused by the prior art Miscellaneous problems improve the simplicity of suspension system control.
  • the air pressure control of the control interface X of the suspension valve is realized, and at the same time, the control of the rigid flexible switching function of the suspension system is realized, and the object of control is changed from a single suspension cylinder. In order to group the suspension cylinders, the control interface is simpler and the control is more convenient.
  • the suspension system of the invention adopts the left and right cross control connection, and the front and rear grouping according to the position of the center of gravity of the vehicle before and after, better supporting the frame and the body of the engineering vehicle, realizing the axle load balancing function of the suspension system, and Conducive to the realization of the fast leveling function.
  • the PLC or the microcomputer control unit 2 can be constituted by other control elements such as a single chip microcomputer and an electronic component; the control mode of the pilot control valve can be realized by electronic control, air control, and hydraulic control; before and after the suspension cylinder is performed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)

Abstract

L'invention porte sur une soupape de suspension, qui comprend une soupape de blocage à commutateur d'entrée d'huile (22), une soupape de blocage à commutateur de retour d'huile (21) et des unités de détection de pression différentielle et de commande logique. Les unités de détection de pression différentielle et de commande logique comprennent un clapet-navette logique (23), une soupape de détection de pression différentielle et de blocage (24) et une soupape de commande de guidage (25). La soupape de blocage à commutateur de retour d'huile (21) peut ouvrir et bloquer le trajet de retour d'huile, et la soupape de blocage à commutateur d'entrée d'huile (22) peut ouvrir et bloquer le trajet d'entrée d'huile. Le clapet-navette logique (23) compare les logiques de pression entre une chambre côté tige d'un cylindre de suspension à huile et une chambre sans tige du cylindre de suspension à huile. La soupape de détection de pression différentielle et de blocage (24) détecte la pression différentielle entre la chambre côté tige du cylindre de suspension à huile et la chambre sans tige du cylindre de suspension à huile, ainsi que relie et bloque les deux chambres. En outre, l'invention porte sur un système de suspension hydropneumatique et sur un véhicule d'ingénierie adoptant ladite soupape de suspension. Par utilisation des unités de détection de pression différentielle et de commande logique, l'invention permet, de manière plus fiable, le maintien pendant longtemps à la fois d'un mode rigide et d'un mode souple du système de suspension, réalise une conversion rapide et fiable entre le mode rigide et le mode souple, réduit efficacement le nombre d'unités dans la soupape de suspension du système de suspension à essieu, permettant ainsi de parvenir à une commande facile et pratique.
PCT/CN2011/074254 2010-08-26 2011-05-18 Soupape de suspension, système de suspension hydropneumatique et véhicule d'ingénierie Ceased WO2012024945A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201010265955.1 2010-08-26
CN 201010265955 CN102039792B (zh) 2010-08-26 2010-08-26 悬挂阀、油气悬架系统及工程车辆

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WO2012024945A1 true WO2012024945A1 (fr) 2012-03-01

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WO (1) WO2012024945A1 (fr)

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CN102039792B (zh) * 2010-08-26 2013-03-20 中联重科股份有限公司 悬挂阀、油气悬架系统及工程车辆
CN102991296B (zh) * 2011-09-19 2015-03-18 北汽福田汽车股份有限公司 油气悬挂装置、油气悬架、底盘和车辆
CN102632787B (zh) * 2012-02-27 2014-09-10 三一汽车制造有限公司 平衡悬架系统、工程车辆及缓冲缸
CN103204042B (zh) * 2012-12-28 2016-06-08 中联重科股份有限公司 压力平衡装置、油气悬挂自动调平系统及工程车辆
CN103552438B (zh) * 2013-10-29 2016-03-02 中联重科股份有限公司 油气悬挂系统及其控制方法、工程车辆
CN103600634B (zh) * 2013-11-25 2015-12-16 徐州重型机械有限公司 钻机车专用底盘
CN103953680B (zh) * 2014-03-20 2016-08-17 中国北方车辆研究所 模块化可调悬挂温度补偿系统
CN105365521B (zh) * 2015-11-30 2018-09-14 中联重科股份有限公司 悬架阀组、油气悬架控制系统和方法及车辆
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CN106183685B (zh) * 2016-08-18 2018-09-18 北京航天发射技术研究所 悬挂系统、车身稳定系统及汽车
CN106394159B (zh) * 2016-10-25 2018-12-21 张家口舒狮汽车科技有限公司 车辆悬架和车辆
CN109131565A (zh) * 2018-09-06 2019-01-04 陕西同力重工股份有限公司 非公路宽体自卸车
CN109441913B (zh) * 2018-10-18 2020-01-31 中联重科股份有限公司 悬挂阀、悬挂系统及工程车辆
CN109624636B (zh) * 2018-12-12 2020-11-17 中联重科股份有限公司 油气悬架系统和车辆
CN112078316B (zh) * 2020-10-16 2025-01-28 上海图昂科技有限公司 一种油气悬架机构及车辆
CN114135533B (zh) * 2021-11-05 2024-03-29 浙江路得坦摩汽车部件股份有限公司 一种流量敏感型自适应截止阀
CN115159350B (zh) * 2022-06-22 2025-08-01 中联重科股份有限公司 油气悬挂控制阀和油气悬挂液压控制系统

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JPH09315125A (ja) * 1996-03-28 1997-12-09 Toyota Autom Loom Works Ltd 産業車両の制御装置
EP0919124A1 (fr) * 1997-12-02 1999-06-02 Agrifac BV Dispositif d'épandage suspendu à des ressorts
WO2003103996A2 (fr) * 2002-06-04 2003-12-18 Van Der Westhuizen, Jakob, Johannes Systeme de suspension destine a un vehicule
CN2823019Y (zh) * 2005-05-17 2006-10-04 曹洪 汽车悬挂平衡侧力弹性浮动装置
CN102039792A (zh) * 2010-08-26 2011-05-04 长沙中联重工科技发展股份有限公司 悬挂阀、油气悬架系统及工程车辆
CN201856597U (zh) * 2010-08-26 2011-06-08 长沙中联重工科技发展股份有限公司 悬挂阀、油气悬架系统及工程车辆

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09315125A (ja) * 1996-03-28 1997-12-09 Toyota Autom Loom Works Ltd 産業車両の制御装置
EP0919124A1 (fr) * 1997-12-02 1999-06-02 Agrifac BV Dispositif d'épandage suspendu à des ressorts
WO2003103996A2 (fr) * 2002-06-04 2003-12-18 Van Der Westhuizen, Jakob, Johannes Systeme de suspension destine a un vehicule
CN2823019Y (zh) * 2005-05-17 2006-10-04 曹洪 汽车悬挂平衡侧力弹性浮动装置
CN102039792A (zh) * 2010-08-26 2011-05-04 长沙中联重工科技发展股份有限公司 悬挂阀、油气悬架系统及工程车辆
CN201856597U (zh) * 2010-08-26 2011-06-08 长沙中联重工科技发展股份有限公司 悬挂阀、油气悬架系统及工程车辆

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CN102039792B (zh) 2013-03-20

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