CN108006220A - Pneumatic hydraulic speed control system - Google Patents

Pneumatic hydraulic speed control system Download PDF

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Publication number
CN108006220A
CN108006220A CN201711493117.8A CN201711493117A CN108006220A CN 108006220 A CN108006220 A CN 108006220A CN 201711493117 A CN201711493117 A CN 201711493117A CN 108006220 A CN108006220 A CN 108006220A
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China
Prior art keywords
valve
control
control valve
freewheel
driving
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Granted
Application number
CN201711493117.8A
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Chinese (zh)
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CN108006220B (en
Inventor
卢明立
封新海
苗增
周爱斌
赵国洋
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Jiangsu Tianming Special Vehicle Co Ltd
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Jiangsu Tianming Special Vehicle Co Ltd
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Publication of CN108006220A publication Critical patent/CN108006220A/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38Control of exclusively fluid gearing
    • F16H61/40Control of exclusively fluid gearing hydrostatic
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38Control of exclusively fluid gearing
    • F16H61/40Control of exclusively fluid gearing hydrostatic
    • F16H61/4192Detecting malfunction or potential malfunction, e.g. fail safe
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38Control of exclusively fluid gearing
    • F16H61/40Control of exclusively fluid gearing hydrostatic
    • F16H61/42Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38Control of exclusively fluid gearing
    • F16H61/40Control of exclusively fluid gearing hydrostatic
    • F16H61/44Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Fluid Gearings (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The present invention is a kind of Pneumatic hydraulic speed control system, including control module and controlled module, controlled module includes some drive wheel groups, each driving group wheel is equipped with two wheels, every wheel is all driven by a two point form variable hydraulic motor, every motor, which is equipped with, becomes displacement control mouth and oil inlet A, B, and oil inlet A, B are respectively by driving oil pipe to connect with driving oil circuit manifold A, B;Drive wheel group includes conventional wheel group and freewheel group, driven in freewheel group every wheel motor driving oil pipe on be equipped with free wheel drive valve;Control module includes total position valve, half displacement control valve and freewheel control valve;The delivery outlet of total position valve connects with the driving mouth of half displacement control valve and freewheel control valve;The control liquid outlet of half displacement control valve is connected by pipeline with the change displacement control mouth of every motor;The control liquid outlet of freewheel control valve is connected by pipeline with the driving mouth of every free wheel drive valve.

Description

Pneumatic hydraulic speed control system
Technical field
The present invention relates to a kind of speed control system of mining special haulage vehicle, particularly a kind of Pneumatic hydraulic speed control System processed.
Background technology
Common haulage equipment of the underground coal mine transport by the use of flat bed transport vehicle as mining Material Transportation, in underground material transfer During played an important role.Go deep into the modernization restructuring of production facility of coalmine, large coal mine manufacturing enterprise Production automation degree is higher and higher.In order to which large coal mine winning apparatus is transported to underground work face, it is necessary to dedicated auxiliary Transporting equipment.
In order to meet the particular/special requirement of underground coal mine transport, hydraulic power carrier comes into being, and solves large-scale exploitation The problem of equipment underground transportation.But have also discovered some problems in actual use, such as:Hydraulic power carrier is automatically controlled System failure rate is high, no-load speed carries to come up, and when carrier breaks down, vehicle dragging is difficult, is easily caused in dragging process Hydraulic motor damage etc., these problems demands solve.
The content of the invention
The technical problems to be solved by the invention are in view of the deficiencies of the prior art, there is provided a kind of failure rate is low and efficient section The Pneumatic hydraulic speed control system of energy.
The technical problems to be solved by the invention are realized by following technical solution.The present invention is a kind of pneumatic Hydraulic speed control system, its main feature is that:Including control module and controlled module,
The controlled module includes some drive wheel groups, and each driving group wheel is equipped with symmetrical two wheels, every wheel All driven by two point form variable hydraulic motor, every two point form variable hydraulic motor be equipped with become displacement control mouth and into Hydraulic fluid port A, B, the oil inlet A, oil inlet B are respectively by driving oil pipe to connect with driving oil circuit manifold A, driving oil circuit manifold B; Above-mentioned drive wheel group includes conventional wheel group and freewheel group, and the two point form variable hydraulic motor of every wheel is driven in freewheel group Driving oil pipe on be equipped with a free wheel drive valve, the free wheel drive valve includes turning on and disconnecting two stations;
The control module includes total position valve, half displacement control valve and freewheel control valve, half displacement control valve and freewheel control Valve processed is equipped with driving mouth, control liquid import and the outlet of control liquid;The delivery outlet and half displacement control valve and oneself of total position valve Connected by the driving mouth of wheel control valve;The control liquid outlet of half displacement control valve is become by pipeline and above-mentioned every two point form The change displacement control mouth of amount hydraulic motor is connected;The control liquid outlet of the freewheel control valve passes through pipeline and every freewheel The driving mouth of driving valve is connected;
Above-mentioned total position valve is equipped with low-grade, middle-grade and high-grade three step velocitys switching station;
Low-grade station:The valve output of total position is interrupted, and half displacement control valve and freewheel control valve are exported without control signal, and two point form becomes Amount hydraulic motor is in delivery working status, and driving force is maximum;
Middle-grade station:Total position double of displacement control valve of valve produces driving force, and half displacement control valve exports half displacement signal to 2 points The change displacement control mouth of formula variable hydraulic motor, free wheel drive valve is positioned at conducting station, all two point form variable hydraulic motors It is in half displacement operation state;
High-grade station:Double of displacement control valve and freewheel control valve produce driving force, two point form variable delivery hydraulic to total position valve at the same time Motor keeps half displacement operation state;Freewheel control valve output control signal gives free wheel drive valve, and free wheel drive valve changes To station is disconnected, corresponding freewheel group is in off working state.
The technical problems to be solved by the invention can also further be realized by following technical solution.In above institute In a kind of Pneumatic hydraulic speed control system stated:Total position valve is speed control valve, and the driving mouth of speed control valve connects There is control source of the gas;Half displacement control valve and freewheel control valve are pneumatic control hydraulic reversing valve.
The technical problems to be solved by the invention can also further be realized by following technical solution.In above institute In a kind of Pneumatic hydraulic speed control system stated:Total position valve is hydraulic control lever, the driving mouth of hydraulic control lever Connect with control liquid feeding pipe, realize all-hydraulic control.
The technical problems to be solved by the invention can also further be realized by following technical solution.In above institute In a kind of Pneumatic hydraulic speed control system stated:Drive to be equipped with to be used to control between oil circuit manifold A and driving oil circuit manifold B and drive The conducting ball valve of on off operating mode between dynamic oil circuit manifold A, B.
The present invention, according to the load condition of hydraulic power carrier, passes through control by designing controlled module and control module Hydraulic powered plate transport vehicle is switched to suitable notch speed by molding total position valve in the block, is realized in low-speed heave-load, middling speed and is carried, is high The use demand of fast underloading, to reach most efficient carrying state;Designed, and set by the difference of conventional wheel group and freewheel group Half displacement control valve and freewheel control valve, realize the transmission of half displacement control signal and freewheel control signal, realize to horse Up to the control of working status and freewheel working status;By setting ball valve, solve hydraulic powered plate transport vehicle and breaking down Shi Wufa moves problem, avoids causing hydraulic motor to damage.Compared with prior art, the present invention can effectively reduce hydraulic power The failure rate of carrier, improves work efficiency, meets the actual demand of underground coal mine transport.
Brief description of the drawings
Fig. 1 is a kind of structure diagram of the present invention;
Fig. 2 is a kind of structure diagram of alternative solution of Fig. 1;
In figure:1st, total position valve;2nd, half displacement control valve;3rd, freewheel control valve;4th, free wheel drive valve;5th, two point form variable liquid Pressure motor;6th, ball valve.
Embodiment
Concrete technical scheme of the invention described further below, in order to which those skilled in the art is further understood that The present invention, without forming the limitation to its right.
With reference to Fig. 1-2, a kind of Pneumatic hydraulic speed control system, including control module and controlled module,
The controlled module includes some drive wheel groups, and each driving group wheel is equipped with symmetrical two wheels, every wheel All driven by a two point form variable hydraulic motor 5, every two point form variable hydraulic motor 5 be equipped with become displacement control mouth and Oil inlet A, B, the oil inlet A, oil inlet B are respectively by driving oil pipe and driving oil circuit manifold A, driving oil circuit manifold B phases Connect;Above-mentioned drive wheel group includes conventional wheel group and freewheel group, and the two point form variable delivery hydraulic of every wheel is driven in freewheel group A free wheel drive valve 4 is equipped with the driving oil pipe of motor 5, the free wheel drive valve 4 includes turning on and disconnection two Station;
The control module includes total position valve 1, half displacement control valve 2 and freewheel control valve 3, half displacement control valve 2 and freedom Wheel control valve 3 is equipped with driving mouth, control liquid import and the outlet of control liquid;The delivery outlet and half displacement control of total position valve 1 The driving mouth of valve 2 and freewheel control valve 3 connects;The control liquid outlet of half displacement control valve 2 by pipeline with it is above-mentioned every The change displacement control mouth of platform two point form variable hydraulic motor 5 is connected;The control liquid outlet of the freewheel control valve 3 passes through pipeline It is connected with the driving mouth of every free wheel drive valve 4;
Above-mentioned total position valve 1 is equipped with low-grade, middle-grade and high-grade three step velocitys switching station;
Low-grade station:Total position valve 1, which exports, to interrupt, and half displacement control valve 2 and freewheel control valve 3 are exported without control signal, 2 points Formula variable hydraulic motor 5 is in delivery working status, and driving force is maximum;
Middle-grade station:Total position valve 1 produces half displacement control valve 2 driving force, and half displacement control valve 2 exports half displacement signal to two The change displacement control mouth of point type variable hydraulic motor 5, free wheel drive valve 4 is positioned at conducting station, all two point form variable delivery hydraulics Motor 5 is in half displacement operation state;
High-grade station:Total position valve 1 while double of displacement control valve 2 and the generation driving force of freewheel control valve 3, two point form variable liquid Pressure motor 5 keeps half displacement operation state;3 output control signal of freewheel control valve gives free wheel drive valve 4, free wheel drive The commutation of valve 4 is in off working state to station, corresponding freewheel group is disconnected;
Total position valve 1 is speed control valve, and the driving mouth of speed control valve is communicated with control source of the gas;Half displacement control valve 2 and freewheel control valve 3 be pneumatic control hydraulic reversing valve;
Total position valve 1 is hydraulic control lever, and the driving mouth of hydraulic control lever connects with control liquid feeding pipe, realizes complete Hydraulic control;
Drive to be equipped between oil circuit manifold A and driving oil circuit manifold B and be used to control on off operating mode between driving oil circuit manifold A, B Turn on ball valve 6.
A kind of Pneumatic hydraulic speed control system proposed by the present invention, mainly by total position valve 1;Half displacement control valve 2;Freely Take turns control valve 3;Free wheel drive valve 4;Two point form variable hydraulic motor 5;The grade of ball valve 6 part forms(In diagram, alphabetical P is represented Control liquid supplies entrance;Tee represents hydraulic oil-returning mouth;Alphabetical K1 represents the control liquid outlet of half displacement control valve 2;Alphabetical K2 tables Show the control liquid outlet of freewheel control valve 3;Alphabetical K represents the change displacement control mouth of two point form variable hydraulic motor 5;Alphabetical A, B represents driving oil circuit manifold).Functions are as follows:
Total position valve 1:Total position valve 1 is using the compressed air of engine on hydraulic powered plate transport vehicle as control source of the gas(Fig. 1 shows Go out), control source of the gas is connected with the V mouths of total position valve 1, when total position valve 1 is in left position, half displacement control valve 2 and freewheel control The driving mouth of valve 3 is communicated by WX, YZ mouth of total position valve 1 with air, and system is in low or first gear working status;At total position valve 1 When centre position, control source of the gas acts on half displacement control valve 2 by VY mouthfuls, and K1 sends half displacement control signal, at system In mid ranger working status, hydraulic powered plate transport vehicle speed doubles;When total position valve 1 is in right position, system is in Top gear working status, hydraulic powered plate transport vehicle speed double again;Driver can cut according to car load size Gear shift position, to meet the transport requirement of low-speed heave-load, high speed light loading.
Half displacement control valve 2:Half displacement control valve 2 is a kind of two-bit triplet reversal valve, when it drives mouth to have pressure gas source During signal, half displacement control valve 2 switches to left position work, and control liquid passes through half displacement control for the control liquid being passed through at entrance P Valve 2 makes each two point form variable hydraulic motor 5 of hydraulic powered plate transport vehicle be in half displacement operation shape from K1 mouthfuls of outputs State, and then transport vehicle speed doubles;When the driving mouth no pressure source of the gas signal function of half displacement control valve 2, half discharge capacity Control valve 2 switches to right position work, and the signal output of K1 is related with the working status of freewheel control valve 3 at this time.
Freewheel control valve 3:3 operation principle of freewheel control valve is the same as half displacement control valve 2.At freewheel control valve 3 When top gear working status, the output of freewheel control valve 3 by K1 and K2 realize respectively half discharge capacity of haulage vehicle with And freewheel controls, speed doubles again on the basis of mid ranger at this time, meets the requirement of vehicle underloading high speed.
Free wheel drive valve 4:Free wheel drive valve 4 acts on A, B mouth of two point form variable hydraulic motor 5.At system When low or first gear and mid ranger working status, K2 mouthfuls export without freewheel control signal, and free wheel drive valve 4 is in the work of right position State, each two point form variable hydraulic motor 5 of transport vehicle are involved in driving, and meet low-speed heave-load working condition requirement;At system When top gear working status, K2 mouthfuls have the output of freewheel control signal, and free wheel drive valve 4 is in left position working status, drives The two point form variable hydraulic motor 5 of dynamic freewheel is in free state, is not involved in driving, and transport vehicle speed improves in original basis One times;
Two point form variable hydraulic motor 5:Two point form variable hydraulic motor 5 uses two point variable formulas, by becoming displacement control mouth K controls The discharge capacity of motor processed.When the half displacement control signal function that K1 is sent is in the control mouth K of two point form variable hydraulic motor 5, two Point type variable hydraulic motor 5 is in half displacement operation state, and transport vehicle speed doubles;When two point form variable hydraulic motor 5 Change displacement control mouth K when being acted on without control signal, two point form variable hydraulic motor 5 is in delivery working status, at this time two 5 rotating speed of point type variable hydraulic motor reduces, moment of torsion improves, and meets vehicle low-speed heave-load requirement.
Ball valve 6:Ball valve 6 is acted between driving oil circuit manifold A, the B of two point form variable hydraulic motor 5, control oil circuit A, B Break-make.When driver for vehicle breaks down(Such as engine failure), vehicle can not normally travel when, ball valve 6 can be opened, Make to turn between driving oil circuit manifold A, B, this addresses the problem hydraulic powered plate transport vehicle to break down and can not move, and makes Into the phenomenon of driving hydraulic motor damage;Need to close ball valve 6 when hydraulic powered plate transport vehicle works normally, otherwise transport Car can not normally travel.
The operation principle of the system:Total position valve 1 controls the speed of hydraulic powered plate transport vehicle, make vehicle be divided into low speed, Middling speed, at a high speed three kinds of operating modes.Low-speed mode can be used when the vehicle is fully laden, and K1, K2 are exported without control signal at this time, and two point form becomes Amount hydraulic motor 5 is in delivery state, and system speed is most slow, and driving force is maximum;In being used when vehicle medium load Fast mode, half displacement control signal of K1 outputs at this time, two point form variable hydraulic motor 5 are in half displacement condition, system speed Double, driving force reduces half;Fast mode can be used when the vehicle is unladen, at this time K1, K2 export respectively half discharge capacity and Freewheel control signal, two point form variable hydraulic motor 5 are in half displacement condition, and front driving wheel is changed into freewheel and does not provide drive Power, system speed double again, and driving force further reduces.Vehicle low speed weight can be met by the switching of above speed Carry, the working condition requirement such as load and high speed light loading in middling speed, improve the work efficiency of hydraulic powered plate transport vehicle.
Above-mentioned total position valve 1, half displacement control valve 2 and freewheel control valve 3, can be selected the speed control shown in Fig. 1 Valve, pneumatic control hydraulic reversing valve and pneumatic control hydraulic reversing valve, also can be selected hydraulic control lever, liquid controlled reversing shown in Fig. 2 Valve and pilot operated directional control valve replace, and all-hydraulic control mode shown in Fig. 2 can also realize same function.
Compared with prior art, the present invention can effectively reduce the failure rate of hydraulic power carrier, improve work efficiency, this Invention system uses two kinds of working medias of compressed air and hydraulic pressure(It is or all-hydraulic), there is anti-explosion safety, the wet environment of resistance to underground The advantages that.Installing the hydraulic power carrier failure rate of the system significantly reduces, meanwhile, the empty wagons speed of service improves nearly twice, Haulage time is greatly saved.

Claims (4)

  1. A kind of 1. Pneumatic hydraulic speed control system, it is characterised in that:Including control module and controlled module,
    The controlled module includes some drive wheel groups, and each driving group wheel is equipped with symmetrical two wheels, every wheel All driven by two point form variable hydraulic motor, every two point form variable hydraulic motor be equipped with become displacement control mouth and into Hydraulic fluid port A, B, the oil inlet A, oil inlet B are respectively by driving oil pipe to connect with driving oil circuit manifold A, driving oil circuit manifold B; Above-mentioned drive wheel group includes conventional wheel group and freewheel group, and the two point form variable hydraulic motor of every wheel is driven in freewheel group Driving oil pipe on be equipped with a free wheel drive valve, the free wheel drive valve includes turning on and disconnecting two stations;
    The control module includes total position valve, half displacement control valve and freewheel control valve, half displacement control valve and freewheel control Valve processed is equipped with driving mouth, control liquid import and the outlet of control liquid;The delivery outlet and half displacement control valve and oneself of total position valve Connected by the driving mouth of wheel control valve;The control liquid outlet of half displacement control valve is become by pipeline and above-mentioned every two point form The change displacement control mouth of amount hydraulic motor is connected;The control liquid outlet of the freewheel control valve passes through pipeline and every freewheel The driving mouth of driving valve is connected;
    Above-mentioned total position valve is equipped with low-grade, middle-grade and high-grade three step velocitys switching station;
    Low-grade station:The valve output of total position is interrupted, and half displacement control valve and freewheel control valve are exported without control signal, and two point form becomes Amount hydraulic motor is in delivery working status, and driving force is maximum;
    Middle-grade station:Total position double of displacement control valve of valve produces driving force, and half displacement control valve exports half displacement signal to 2 points The change displacement control mouth of formula variable hydraulic motor, free wheel drive valve is positioned at conducting station, all two point form variable hydraulic motors It is in half displacement operation state;
    High-grade station:Double of displacement control valve and freewheel control valve produce driving force, two point form variable delivery hydraulic to total position valve at the same time Motor keeps half displacement operation state;Freewheel control valve output control signal gives free wheel drive valve, and free wheel drive valve changes To station is disconnected, corresponding freewheel group is in off working state.
  2. A kind of 2. Pneumatic hydraulic speed control system according to claim 1, it is characterised in that:Total position valve is speed Control valve, the driving mouth of speed control valve are communicated with control source of the gas;Half displacement control valve and freewheel control valve are gas Control hydraulic directional control valve.
  3. A kind of 3. Pneumatic hydraulic speed control system according to claim 1, it is characterised in that:Total position valve is hydraulic pressure Joystick, the driving mouth of hydraulic control lever connect with control liquid feeding pipe, realize all-hydraulic control.
  4. A kind of 4. Pneumatic hydraulic speed control system according to claim 1, it is characterised in that:Drive oil circuit manifold A with The conducting ball valve for being used for controlling on off operating mode between driving oil circuit manifold A, B is equipped between driving oil circuit manifold B.
CN201711493117.8A 2017-12-30 2017-12-30 Pneumatic hydraulic speed control system Active CN108006220B (en)

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Application Number Priority Date Filing Date Title
CN201711493117.8A CN108006220B (en) 2017-12-30 2017-12-30 Pneumatic hydraulic speed control system

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Application Number Priority Date Filing Date Title
CN201711493117.8A CN108006220B (en) 2017-12-30 2017-12-30 Pneumatic hydraulic speed control system

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CN108006220B CN108006220B (en) 2024-06-21

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH453099A (en) * 1966-06-27 1968-05-31 Simit Societa Per Azioni System with hydraulic transmission for propulsion of vehicles at different speeds
WO1994009294A1 (en) * 1992-10-09 1994-04-28 Hydromatik Gmbh Control device of a hydrostatic transmission with brake valve
CN1187867A (en) * 1995-05-23 1998-07-15 株式会社小松制作所 Capacity control device for hydraulic motor for hydraulically driven vehicle
CN103273843A (en) * 2013-04-27 2013-09-04 燕山大学 Hydraulic part time four-wheel-drive drive system of self-propelled harvester
CN103442923A (en) * 2010-12-01 2013-12-11 罗伯特·博世有限公司 Hydrostatic drive
CN107448425A (en) * 2017-07-21 2017-12-08 广西柳工机械股份有限公司 Control valve and land leveller front wheel driven hydraulic system
CN207945283U (en) * 2017-12-30 2018-10-09 江苏天明特种车辆有限公司 A kind of Pneumatic hydraulic speed control system

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH453099A (en) * 1966-06-27 1968-05-31 Simit Societa Per Azioni System with hydraulic transmission for propulsion of vehicles at different speeds
WO1994009294A1 (en) * 1992-10-09 1994-04-28 Hydromatik Gmbh Control device of a hydrostatic transmission with brake valve
CN1187867A (en) * 1995-05-23 1998-07-15 株式会社小松制作所 Capacity control device for hydraulic motor for hydraulically driven vehicle
CN103442923A (en) * 2010-12-01 2013-12-11 罗伯特·博世有限公司 Hydrostatic drive
CN103273843A (en) * 2013-04-27 2013-09-04 燕山大学 Hydraulic part time four-wheel-drive drive system of self-propelled harvester
CN107448425A (en) * 2017-07-21 2017-12-08 广西柳工机械股份有限公司 Control valve and land leveller front wheel driven hydraulic system
CN207945283U (en) * 2017-12-30 2018-10-09 江苏天明特种车辆有限公司 A kind of Pneumatic hydraulic speed control system

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