CN201694192U - Hydraulic low speed traveling transmission system - Google Patents
Hydraulic low speed traveling transmission system Download PDFInfo
- Publication number
- CN201694192U CN201694192U CN201020131422XU CN201020131422U CN201694192U CN 201694192 U CN201694192 U CN 201694192U CN 201020131422X U CN201020131422X U CN 201020131422XU CN 201020131422 U CN201020131422 U CN 201020131422U CN 201694192 U CN201694192 U CN 201694192U
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Abstract
A hydraulic low speed traveling transmission system adopts the scheme that the oil pump thereof is connected with the inlet of an electro-hydraulic directional valve through a pipeline and the higher and lower working oil ports of the electro-hydraulic directional valve are connected with the oil inlet and the oil outlet of a hydraulic motor respectively; the oil return port of the electro-hydraulic directional valve is communicated with a hydraulic oil tank; and the hydraulic motor is in transmission connection with the gearbox of an axletree. In the traveling process, the oil outlet of the hydraulic motor is communicated with the low-pressure work oil port of the electro-hydraulic directional valve always and never enters the oil inlet pipeline of the oil pump any more, so that the energy obtained from the hydraulic motor in downgrading can not be transmitted to the oil pump and a diesel to cause the rotational speed rise of the diesel; an electric proportional overflow valve is arranged between the oil return port of the electro-hydraulic directional valve and the hydraulic oil tank, so that the return oil pressure on the hydraulic motor can be changed through regulating the electric proportional overflow valve, thereby achieving equilibrium forces on the vehicle, and further, uniform-speed traveling of the vehicle can be realized; and a non-return valve is arranged between the oil inlet and outlet of the hydraulic motor and the oil return pipe of the electric proportional overflow valve, so as to prevent air suction of the hydraulic motor in an open hydraulic system.
Description
Technical field
The utility model relates to a kind of even low speed walking system of hydraulic pressure of railway track polishing vehicle, is a kind of driving system that adopts open type hydraulic system to come the powered vehicle traveling specifically.
Background technology
At present, railway track vehicle low speed traveling both at home and abroad all adopts the hydraulic closed system to realize that traveling drives, and the oil circuit trend is from oil pump → HM Hydraulic Motor → oil pump, forms a closed-cycle system.The drawback that adopts closed system to bring is that vehicle speed of a motor vehicle when " growing up " down ramp moves can increase, and oil pump becomes " motor " operating mode, and motor becomes " oil pump " operating mode, and the height pressure side of pipeline is exchanged.In like manner vehicle the change working of oil pump and motor can occur equally in the decelerating phase, and the height pressure side of pipeline is exchanged equally.To the diesel engine acting, the power that diesel engine absorbs the oil pump input can make the rotating speed of diesel engine raise even can surpass the diesel engine limit speed, easily causes damage diesel engine accident behind the transfer of energy fuel feed pump that motor obtained in down ramp or decelerating phase.
Summary of the invention
The utility model provides a kind of vehicle even low speed walking under various ramps that realizes, avoids vehicle in long heavy down grade or the decelerating phase vehicle inertia hydraulic low-speed traveling driving system to the driving engine acting.
The technical solution of the utility model is to comprise the oil pump of a feed system fluid after the 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.
The return opening into and out of being connected of hydraulic fluid port, electro-hydraulic reversing valve of high and low two actuator ports of said electro-hydraulic reversing valve and HM Hydraulic Motor 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 links to each other 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 the electro-hydraulic reversing valve return opening, be connected with hydraulic reservoir through electric proportional pressure control valve, first by pass valve, cooling mechanism.
Said HM Hydraulic Motor between hydraulic fluid port and electric proportional pressure control valve oil return line, a passage is arranged, on this passage, check valve is housed.
Said oil pump is connected with hydraulic reservoir through second by pass valve.
The oil outlet of the utility model HM Hydraulic Motor in the 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 that obtains in the descending HM Hydraulic Motor can not pass to oil pump, also just can 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, be provided with electric proportional pressure control valve between the return opening of electro-hydraulic reversing valve and the hydraulic reservoir, change the spill pressure that acts on the HM Hydraulic Motor by adjusting electric proportional pressure control valve, reach the vehicle stress balance, guarantee at the uniform velocity traveling of vehicle.Between HM Hydraulic Motor oil inlet and outlet and electric proportional pressure control valve oil return line, be provided with check valve, can prevent the problem that HM Hydraulic Motor is prone in the open type hydraulic system " inhaling empty ".
The utility model has solved the vehicle problem that oil pump " is inhaled empty " when down ramp or decelerating phase operation.Can be implemented under the various ramps vehicle and be in even low speed traveling.
Description of drawings
The embodiment that provides below in conjunction with accompanying drawing is described in further detail the utility model.
Fig. 1 is the utility model hydraulic schematic diagram.
Fig. 2 installs front view for the utility model.
Fig. 3 installs birds-eye view for the utility model.
The specific embodiment
Among Fig. 1, by hydraulic oil pump 10, pilot-operated type second by pass valve 9 (pilot overflow valve), play that the control vehicle advances or the electro-hydraulic reversing valve 3, electric proportional pressure control valve 2, check valve 1, the HM Hydraulic Motor 4 that can promote travelled by vehicle under the pressure oil effect, cooling mechanism 8, fuel tank 6, Direct Action Type the 3rd by pass valve 5 that retreat effect formed an open type hydraulic system loop.Electro-hydraulic reversing valve 3 has two actuator ports, wherein any one is used for the high-pressure work hydraulic fluid port, and then another is used for the operating on low voltage hydraulic fluid port, two hydraulic fluid ports of HM Hydraulic Motor, oil inlet links to each other with the high-pressure work hydraulic fluid port of electro-hydraulic reversing valve, and oil outlet links to each other with the operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve.Two oil pumps 10 collaborate after pipeline is connected with the import P of electro-hydraulic reversing valve 3, after electro-hydraulic reversing valve 3 (band pilot stage solenoid directional control valve) the left end electromagnet energising, fluid is connected with the oil inlet of HM Hydraulic Motor 4 after by the high-pressure work hydraulic fluid port of the left end of electro-hydraulic reversing valve 3, HM Hydraulic Motor 4 oil outlets with after the operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve 3 right-hand members is connected through the oil return inlet T of electro-hydraulic reversing valve.With should electro-hydraulic reversing valve pilot stage solenoid directional control valve right-hand member electromagnet energising back fluid be connected with the oil inlet (former oil outlet becomes oil inlet) of HM Hydraulic Motor 4 after by the high-pressure work hydraulic fluid port of the right-hand member of electro-hydraulic reversing valve 3, HM Hydraulic Motor 4 oil outlets (former oil inlet becomes oil outlet) with after the operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve 3 left ends is connected through the oil return inlet T of electro-hydraulic reversing valve.Fluid enters the oil inlet that can change the electric proportional pressure control valve 2 of constantly adjusting force value according to the speed of a motor vehicle after the electro-hydraulic reversing valve oil return inlet T, after flowing out, enter the oil inlet of first by pass valve 7, flow out from the oil outlet of first by pass valve 7 and enter cooling mechanism 8 backs and be connected with fuel tank 6 from the oil outlet of electric proportional pressure control valve 2.On the oil return line between electric proportional pressure control valve 2 oil outlets and first by pass valve, 7 oil inlets, there is a passage to be connected with the HM Hydraulic Motor oil inlet, check valve 1 is housed on this passage.Oil pump 10 oil outlets are connected with fuel tank 6 after having a passage to enter second by pass valve, 9 oil inlets.The pipeline that the 3rd by pass valve 5 is loaded on the high-pressure work hydraulic fluid port of electro-hydraulic reversing valve 3 and HM Hydraulic Motor 4 oil inlets is between the pipeline of the operating on low voltage hydraulic fluid port of electro-hydraulic reversing valve 3 and HM Hydraulic Motor 4 oil outlets.
When down ramp moves, the even low speed of vehicle realizes it being the force value of constantly adjusting electric proportional pressure control valve 2 according to the variation of the speed of a motor vehicle, this pressure acts on the oil outlet of HM Hydraulic Motor after by electro-hydraulic reversing valve, act on the motor gear case after applying a reactive torque to HM Hydraulic Motor, this reactive torque is offset vehicle gravity along the component on the ramp to producing an antagonistic force on the vehicle after passing to transmission shaft and axle gear box, reaches the state of traveling at the uniform speed until the vehicle stress balance.When hypervelocity appears in down ramp or decelerating phase vehicle, oil pump and HM Hydraulic Motor are carried out change working, by check valve 1 oil revolving end fluid is oppositely supplied with oil inlet when the fuel feeding deficiency appears in oil inlet after HM Hydraulic Motor change " oil pump " operating mode, avoid HM Hydraulic Motor to be in and " inhale that empty " state, charge oil pressure is adjusted by first by pass valve 7.The 3rd by pass valve 5 is used for eliminating the spike pressure of traveling HM Hydraulic Motor oil inlet end, prevents the HM Hydraulic Motor impact that is under pressure.
Oil circuit trend: 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 valves 9 → cooling mechanism 8 → fuel tank 6
Among Fig. 2, Fig. 3, said HM Hydraulic Motor 4 places on the carriage frame 11 below motor gear casees 20, motor gear case 20 mouths are connected with second transmission shaft 19, second transmission shaft 19 is connected with second axle gear box 18, and second axle gear box 18 and first axle gear box 16 are connected together through the 3rd transmission shaft 17.Oil pump 10 is installed in auxiliary gear box 14 1 sides, auxiliary gear box 14 opposite sides and is installed in diesel engine 12 rear ends after first transmission shaft 13 is connected.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 is all integrated is installed on the vehicle frame 11 top integrated packages 15.Said cooling mechanism 8 is installed in vehicle frame 11 tops, and first by pass valve 7 is installed in the cooling mechanism side.Fuel tank 6 is installed in vehicle frame 11 tops.
Claims (4)
1. hydraulic low-speed traveling driving system is characterized in that: the oil pump that comprises a feed system fluid after the 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; Said HM Hydraulic Motor between hydraulic fluid port and electric proportional pressure control valve oil return line, a passage is arranged, on this passage, check valve is housed.
2. hydraulic low-speed traveling driving system according to claim 1 is characterized in that: high and low two actuator ports of said 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 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 links to each other 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 the electro-hydraulic reversing valve return opening, be connected with hydraulic reservoir through electric proportional pressure control valve, first by pass valve, cooling mechanism.
3. hydraulic low-speed traveling driving system according to claim 1, it is characterized in that: said oil pump is connected with hydraulic reservoir through second by pass valve.
4. hydraulic low-speed traveling driving system according to claim 1, it is characterized in that: being in transmission connection of said HM Hydraulic Motor and axle gear box places on the motor gear case of carriage frame below for: HM Hydraulic Motor, motor gear case mouth is connected with second transmission shaft, second transmission shaft is connected with second axle gear box, and second axle gear box is connected through the 3rd transmission shaft with first axle gear box.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201020131422XU CN201694192U (en) | 2010-02-27 | 2010-02-27 | Hydraulic low speed traveling transmission system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201020131422XU CN201694192U (en) | 2010-02-27 | 2010-02-27 | Hydraulic low speed traveling transmission system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201694192U true CN201694192U (en) | 2011-01-05 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201020131422XU Expired - Lifetime CN201694192U (en) | 2010-02-27 | 2010-02-27 | Hydraulic low speed traveling transmission system |
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| CN (1) | CN201694192U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102167046A (en) * | 2010-02-27 | 2011-08-31 | 襄樊金鹰轨道车辆有限责任公司 | Hydraulic low-speed walking transmission system |
| CN102963457A (en) * | 2012-10-31 | 2013-03-13 | 中国煤炭科工集团太原研究院 | Low-type combination-drive trackless rubber-tire carrier vehicle |
| CN111595594A (en) * | 2020-06-01 | 2020-08-28 | 山东省农业机械科学研究院 | Tractor traction load mobile test system and method |
-
2010
- 2010-02-27 CN CN201020131422XU patent/CN201694192U/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102167046A (en) * | 2010-02-27 | 2011-08-31 | 襄樊金鹰轨道车辆有限责任公司 | Hydraulic low-speed walking transmission system |
| CN102167046B (en) * | 2010-02-27 | 2015-05-20 | 襄樊金鹰轨道车辆有限责任公司 | Hydraulic low-speed walking transmission system |
| CN102963457A (en) * | 2012-10-31 | 2013-03-13 | 中国煤炭科工集团太原研究院 | Low-type combination-drive trackless rubber-tire carrier vehicle |
| CN102963457B (en) * | 2012-10-31 | 2015-09-30 | 中国煤炭科工集团太原研究院 | Short combination drive trackless rubber-tyred transport trolley |
| CN111595594A (en) * | 2020-06-01 | 2020-08-28 | 山东省农业机械科学研究院 | Tractor traction load mobile test system and method |
| CN111595594B (en) * | 2020-06-01 | 2021-07-09 | 山东省农业机械科学研究院 | Tractor traction load mobile test system and method |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20110105 Effective date of abandoning: 20150520 |
|
| RGAV | Abandon patent right to avoid regrant |