CN102167046B - Hydraulic low-speed walking transmission system - Google Patents
Hydraulic low-speed walking transmission system Download PDFInfo
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- CN102167046B CN102167046B CN201010124438.2A CN201010124438A CN102167046B CN 102167046 B CN102167046 B CN 102167046B CN 201010124438 A CN201010124438 A CN 201010124438A CN 102167046 B CN102167046 B CN 102167046B
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Abstract
The invention discloses a hydraulic low-speed walking transmission system. The oil pump of the system is connected with the inlet of an electrohydraulic selector valve by a pipeline; the high pressure working oil port and the low pressure working oil port of the electrohydraulic selector valve are connected with the oil inlet and the oil outlet of a hydraulic motor; the oil returning port of the electrohydraulic selector valve is communicated with a hydraulic oil tank; and the hydraulic motor is in transmission connection with an axle gear box. In the walking process, the oil outlet of the hydraulic motor is always communicated with the low pressure working oil port of the electrohydraulic selector valve, and does not enter the oil inlet pipeline of an oil pump any more. In the descending process, the energy acquired by the hydraulic motor cannot be transferred to the oil pump and a diesel engine, so that the rotational speed of the diesel engine increases. An electric proportional overflow valve is arranged between the oil returning port of the electrohhydraulic selector valve and the hydraulic oil tank, and an oil returning pressure applied to the hydraulic motor is changed by adjusting the electric proportional overflow valve, so that the stress on a vehicle is balanced, and the constant-speed walking of the vehicle is ensured. Check valves are arranged between the oil inlet and the oil outlet of the hydraulic motor and the oil returning pipeline of the electric proportional overflow valve, so that the problem that suction easily occurs in the hydraulic motor in an open hydraulic system can be solved.
Description
Technical field
The present invention relates to a kind of even low speed walking system of hydraulic pressure of railway steel rail polishing vehicle, is that a kind of open type hydraulic system that adopts is to drive the driving system of travelled by vehicle specifically.
Background technology
At present, the traveling of domestic and international railway track vehicle low speed all adopts hydraulic closed system to realize away row cutting, and oil circuit trend is from oil pump → HM Hydraulic Motor → oil pump, forms a closed-cycle system.The drawback adopting closed system to bring is that vehicle speed of a motor vehicle when " growing up " down ramp runs can increase, operating mode that oil pump becomes " motor ", operating mode that motor becomes " oil pump ", and the height pressure side of pipeline is exchanged.In like manner vehicle there will be the change working of oil pump and motor equally in the decelerating phase, and the height pressure side of pipeline is exchanged equally.To diesel engine acting after the energy transferring fuel feed pump that motor obtained in down ramp or decelerating phase, the power that diesel engine absorbs oil pump input can make the rotating speed of diesel engine raise even to exceed diesel engine limit speed, easily cause and damage diesel engine accident.
Summary of the invention
The invention provides one and can realize vehicle even low speed walking under various ramp, avoid the hydraulic low speed traveling transmission system that vehicle does work to driving engine at long heavy down grade or decelerating phase vehicle inertia.
Technical program of the present invention lies in comprising an oil pump from feed system fluid after hydraulic reservoir oil suction; Oil pump is connected with the import of electro-hydraulic reversing valve through pipeline, high and low two actuator ports of electro-hydraulic reversing valve and being connected into and out of hydraulic fluid port of HM Hydraulic Motor; The return opening of electro-hydraulic reversing valve is connected with hydraulic reservoir, and HM Hydraulic Motor and axle gear box are in transmission connection.
High and low two actuator ports of said electro-hydraulic reversing valve with the connection into and out of hydraulic fluid port of HM Hydraulic Motor, the return opening of electro-hydraulic reversing valve with the connection of hydraulic reservoir are: electro-hydraulic reversing valve high-pressure work hydraulic fluid port is connected with the oil inlet of HM Hydraulic Motor through pipeline; The oil outlet of HM Hydraulic Motor is connected with the operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve through pipeline; The operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve is through electro-hydraulic reversing valve return opening, be connected with hydraulic reservoir through electric proportional pressure control valve, the first by pass valve, cooling mechanism.
Said HM Hydraulic Motor have a passage into and out of between hydraulic fluid port and electric proportional pressure control valve oil return line, this passage is equipped with check valve.
Said oil pump is connected with hydraulic reservoir through the second by pass valve.
The oil outlet of the present invention's HM Hydraulic Motor in traveling process communicates with electro-hydraulic reversing valve operating on low voltage hydraulic fluid port all the time, no longer enters on the oil inlet pipeline of oil pump.The energy obtained in descending HM Hydraulic Motor can not pass to oil pump, also would not be delivered to diesel engine and cause the rotating speed of diesel engine to raise.The oil outlet of HM Hydraulic Motor is connected with hydraulic reservoir through the return opening of electro-hydraulic reversing valve, electric proportional pressure control valve is provided with between the return opening of electro-hydraulic reversing valve and hydraulic reservoir, by adjusting electric proportional pressure control valve to change the spill pressure acted in HM Hydraulic Motor, reach vehicle stress balance, ensure that vehicle can at the uniform velocity traveling.Between HM Hydraulic Motor oil inlet and outlet and electric proportional pressure control valve oil return line, be provided with check valve, can prevent HM Hydraulic Motor in open type hydraulic system from easily occurring the problem of " inhaling empty ".
The invention solves the vehicle problem that oil pump " is inhaled empty " when down ramp or decelerating phase run.Vehicle under various ramp can be realized and be in even low speed traveling.
Accompanying drawing explanation
The embodiment provided below in conjunction with accompanying drawing is described in further detail the present invention.
Fig. 1 is hydraulic schematic diagram of the present invention.
Fig. 2 is that the present invention installs front view.
Fig. 3 is that the present invention installs birds-eye view.
Detailed description of the invention
In Fig. 1, form an open type hydraulic system loop by hydraulic oil pump 10, pilot-operated type second by pass valve 9 (pilot overflow valve), the electro-hydraulic reversing valve 3 playing the advance of control vehicle or retrogressing effect, electric proportional pressure control valve 2, check valve 1, the HM Hydraulic Motor 4 that can promote travelled by vehicle under pressure oil effect, cooling mechanism 8, fuel tank 6, Direct Action Type the 3rd by pass valve 5.Electro-hydraulic reversing valve 3 has two actuator ports, wherein any one is for high-pressure work hydraulic fluid port, then another is for operating on low voltage hydraulic fluid port, two hydraulic fluid ports of HM Hydraulic Motor, oil inlet is connected with the high-pressure work hydraulic fluid port of electro-hydraulic reversing valve, and oil outlet is connected with the operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve.Be connected with the import P of electro-hydraulic reversing valve 3 through pipeline after two oil pumps 10 collaborate, after electro-hydraulic reversing valve 3 (band pilot stage solenoid directional control valve) left end electromagnet energising, fluid by being connected with the oil inlet of HM Hydraulic Motor 4 after the high-pressure work hydraulic fluid port of the left end of electro-hydraulic reversing valve 3, through the oil return inlet T of electro-hydraulic reversing valve after HM Hydraulic Motor 4 oil outlet is connected with the operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve 3 right-hand member.With being energized rear fluid by being connected with the oil inlet (former oil outlet becomes oil inlet) of HM Hydraulic Motor 4 after the high-pressure work hydraulic fluid port of the right-hand member of electro-hydraulic reversing valve 3, through the oil return inlet T of electro-hydraulic reversing valve after HM Hydraulic Motor 4 oil outlet (former oil inlet becomes oil outlet) is connected with the operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve 3 left end by electro-hydraulic reversing valve pilot stage solenoid directional control valve right-hand member electromagnet.Fluid enters the oil inlet that constantly can adjust the electric proportional pressure control valve 2 of force value according to speed of a motor vehicle change after electro-hydraulic reversing valve oil return inlet T, after flowing out from the oil outlet of electric proportional pressure control valve 2, enter the oil inlet of the first by pass valve 7, be connected with fuel tank 6 after the oil outlet outflow of the first by pass valve 7 enters cooling mechanism 8.On oil return line between electric proportional pressure control valve 2 oil outlet and the first by pass valve 7 oil inlet, there is a passage to be connected with HM Hydraulic Motor oil inlet, this passage is equipped with check valve 1.Oil pump 10 oil outlet is connected with fuel tank 6 after having a passage to enter the second by pass valve 9 oil inlet.3rd by pass valve 5 is loaded between the high-pressure work hydraulic fluid port of electro-hydraulic reversing valve 3 and the pipeline of HM Hydraulic Motor 4 oil inlet to the operating on low voltage hydraulic fluid port and the pipeline of HM Hydraulic Motor 4 oil outlet of electro-hydraulic reversing valve 3.
When down ramp runs, the even low speed of vehicle realizes being the force value constantly adjusting electric proportional pressure control valve 2 according to the change of the speed of a motor vehicle, this pressure is by acting on the oil outlet of HM Hydraulic Motor after electro-hydraulic reversing valve, act on motor gear roller box after applying a reactive torque to HM Hydraulic Motor, to vehicle producing an antagonistic force to offset vehicle weight along the component on ramp after this reactive torque passes to transmission shaft and axle gear box, until vehicle stress balance reaches the state of traveling at the uniform speed.When there is hypervelocity in down ramp or decelerating phase vehicle, oil pump and HM Hydraulic Motor carry out change working, after HM Hydraulic Motor becomes " oil pump " operating mode, oil inlet occurs by check valve 1, oil revolving end fluid oppositely being supplied oil inlet for during shortage of oil, " " state, charge oil pressure is adjusted by the first by pass valve 7 to inhale sky to avoid HM Hydraulic Motor to be in.3rd by pass valve 5 is used for eliminating the spike pressure of traveling HM Hydraulic Motor oil inlet end, prevents HM Hydraulic Motor to be under pressure impact.
Oil circuit moves towards: fuel tank 6 → oil pump 10 → electro-hydraulic reversing valve 3 → HM Hydraulic Motor 4 → electro-hydraulic reversing valve 3 → electric proportional pressure control valve 2 → the second by pass valve 9 → cooling mechanism 8 → fuel tank 6
In Fig. 2, Fig. 3, said HM Hydraulic Motor 4 to be placed in below carriage frame 11 on motor gear roller box 20, motor gear roller box 20 mouth is connected with second driving shaft 19, second driving shaft 19 is connected with the second axle gear box 18, and the second axle gear box 18 and the first axle gear box 16 are connected together through the 3rd transmission shaft 17.Oil pump 10 is arranged on auxiliary gear box 14 side, auxiliary gear box 14 opposite side is arranged on diesel engine 12 rear end after being connected with the first transmission shaft 13.Said electro-hydraulic reversing valve 3, electric proportional pressure control valve 2, second by pass valve 9, the 3rd by pass valve 5, check valve 1 all integrated installation above vehicle frame 11 on integrated package 15.Said cooling mechanism 8 is arranged on above vehicle frame 11, and the first by pass valve 7 is arranged on cooling mechanism side.Fuel tank 6 is arranged on above vehicle frame 11.
Claims (3)
1. a hydraulic low speed traveling transmission system, is characterized in that: comprise an oil pump from feed system fluid after hydraulic reservoir oil suction; Oil pump is connected with the import of electro-hydraulic reversing valve through pipeline, high and low two actuator ports of electro-hydraulic reversing valve and being connected into and out of hydraulic fluid port of HM Hydraulic Motor; The return opening of electro-hydraulic reversing valve is connected with hydraulic reservoir; HM Hydraulic Motor and axle gear box are in transmission connection; Described HM Hydraulic Motor have a passage into and out of between hydraulic fluid port and electric proportional pressure control valve oil return line, this passage is equipped with check valve;
High and low two actuator ports of described electro-hydraulic reversing valve and the connection into and out of hydraulic fluid port of HM Hydraulic Motor; The return opening of electro-hydraulic reversing valve with the connection of hydraulic reservoir is: electro-hydraulic reversing valve high-pressure work hydraulic fluid port is connected with the oil inlet of HM Hydraulic Motor through pipeline; The oil outlet of HM Hydraulic Motor is connected with the operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve through pipeline, and the operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve is through electro-hydraulic reversing valve return opening, be connected with hydraulic reservoir through electric proportional pressure control valve, the first by pass valve, cooling mechanism.
2. hydraulic low speed traveling transmission system according to claim 1, is characterized in that: described oil pump is connected with hydraulic reservoir through the second by pass valve.
3. hydraulic low speed traveling transmission system according to claim 1, it is characterized in that: described HM Hydraulic Motor and axle gear box be in transmission connection as: HM Hydraulic Motor to be placed in below carriage frame on motor gear roller box, motor gear roller box mouth is connected with second driving shaft, second driving shaft is connected with the second axle gear box, and the second axle gear box is connected through the 3rd transmission shaft with the first axle gear box; Oil pump is arranged on auxiliary gear box side, auxiliary gear box opposite side is arranged on diesel engine rear end after being connected with the first transmission shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010124438.2A CN102167046B (en) | 2010-02-27 | 2010-02-27 | Hydraulic low-speed walking transmission system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010124438.2A CN102167046B (en) | 2010-02-27 | 2010-02-27 | Hydraulic low-speed walking transmission system |
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| CN102167046A CN102167046A (en) | 2011-08-31 |
| CN102167046B true CN102167046B (en) | 2015-05-20 |
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| CN201010124438.2A Active CN102167046B (en) | 2010-02-27 | 2010-02-27 | Hydraulic low-speed walking transmission system |
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| CN102330670B (en) * | 2011-09-19 | 2014-12-10 | 中航力源液压股份有限公司 | Method and device for preventing plunger pump from sucking air |
| CN103213585A (en) * | 2012-07-13 | 2013-07-24 | 金鹰重型工程机械有限公司 | Double-dynamical transmission system of rail vehicle |
| CN103775621A (en) * | 2014-01-22 | 2014-05-07 | 宝鸡南车时代工程机械有限公司 | Railway rail car torque converter reverse drag lubrication system |
| CN104627160A (en) * | 2015-02-13 | 2015-05-20 | 湖南五新重型装备有限公司 | Hydraulic walking control system for engineering vehicle |
| CN104976307A (en) * | 2015-07-16 | 2015-10-14 | 河海大学常州校区 | Hydraulic coupler |
| CN105179632A (en) * | 2015-07-16 | 2015-12-23 | 河海大学常州校区 | Hydraulic coupler |
| CN112682369A (en) * | 2021-01-11 | 2021-04-20 | 中车株洲车辆有限公司 | Dual-purpose vehicle for road and railway, and hydraulic control system and method for dual-purpose vehicle for road and railway |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2026910A1 (en) * | 1970-06-02 | 1971-12-23 | Lucas Ltd Joseph | Hydraulic transmission |
| DE2354280A1 (en) * | 1973-10-30 | 1975-05-15 | Voith Getriebe Kg | High power motor vehicle drive - has mechanical synchronised reversing gear and hydrostatic drive and coupling |
| CN2084407U (en) * | 1990-12-29 | 1991-09-11 | 乌鲁木齐铁路局科学技术研究所 | Spindle bearing nut disassemble machine for diesel engine |
| CN2189570Y (en) * | 1993-05-22 | 1995-02-15 | 铁道部四方机车车辆工厂 | Hydraulic direction-changing mechanism for locomotive |
| CN101492053A (en) * | 2009-02-19 | 2009-07-29 | 肖公平 | Ropeway fluid power system for mine |
| CN201363327Y (en) * | 2009-01-15 | 2009-12-16 | 杭州海聚动力科技有限公司 | Hydraulic system applied to fire rescue motorcycle |
| CN201694192U (en) * | 2010-02-27 | 2011-01-05 | 襄樊金鹰轨道车辆有限责任公司 | Hydraulic low speed traveling transmission system |
-
2010
- 2010-02-27 CN CN201010124438.2A patent/CN102167046B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2026910A1 (en) * | 1970-06-02 | 1971-12-23 | Lucas Ltd Joseph | Hydraulic transmission |
| DE2354280A1 (en) * | 1973-10-30 | 1975-05-15 | Voith Getriebe Kg | High power motor vehicle drive - has mechanical synchronised reversing gear and hydrostatic drive and coupling |
| CN2084407U (en) * | 1990-12-29 | 1991-09-11 | 乌鲁木齐铁路局科学技术研究所 | Spindle bearing nut disassemble machine for diesel engine |
| CN2189570Y (en) * | 1993-05-22 | 1995-02-15 | 铁道部四方机车车辆工厂 | Hydraulic direction-changing mechanism for locomotive |
| CN201363327Y (en) * | 2009-01-15 | 2009-12-16 | 杭州海聚动力科技有限公司 | Hydraulic system applied to fire rescue motorcycle |
| CN101492053A (en) * | 2009-02-19 | 2009-07-29 | 肖公平 | Ropeway fluid power system for mine |
| CN201694192U (en) * | 2010-02-27 | 2011-01-05 | 襄樊金鹰轨道车辆有限责任公司 | Hydraulic low speed traveling transmission system |
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| CN102167046A (en) | 2011-08-31 |
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Address after: 441000 No.1, Xinming Road, high tech Zone, Xiangyang City, Hubei Province Patentee after: Jinying Heavy Construction Machinery Co.,Ltd. Address before: 441001 No.19 Xudong Road, Xiangyang City, Hubei Province Patentee before: GEMAC ENGINEERING MACHINERY Co.,Ltd. Address after: 441001 No.19 Xudong Road, Xiangyang City, Hubei Province Patentee after: GEMAC ENGINEERING MACHINERY Co.,Ltd. Address before: 441001 No. 19 Dongxu East Road, Hubei, Xiangfan Patentee before: Xiangfan Golden Eagle Railway Vehicle & Machinery Co.,Ltd. |
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