CN210859382U - Vehicle running hydraulic control system and vehicle - Google Patents
Vehicle running hydraulic control system and vehicle Download PDFInfo
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- CN210859382U CN210859382U CN201921676182.9U CN201921676182U CN210859382U CN 210859382 U CN210859382 U CN 210859382U CN 201921676182 U CN201921676182 U CN 201921676182U CN 210859382 U CN210859382 U CN 210859382U
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Abstract
The utility model relates to a vehicle control technical field that traveles especially relates to a vehicle hydraulic control system and vehicle that traveles. A hydraulic control system for vehicle running includes a bidirectional variable pump and a bidirectional variable motor constituting a volume speed control loop, and an engine driving the bidirectional variable pump to rotate, a forward oil port of the bidirectional variable pump and a forward oil port of the bidirectional variable motor are communicated through a first oil path, a reverse oil port of the bidirectional variable pump and a reverse oil port of the bidirectional variable motor are communicated through a second oil path, and further includes: the external control type overflow valve bank is connected with the bidirectional variable motor in parallel; the switch valve bank is arranged between the external control type overflow valve bank and the oil tank; the first overflow valve is arranged between the switch valve group and the oil tank. When the vehicle is switched to the automatic sliding mode, the state of the switch valve is firstly adjusted to enable the bidirectional variable pump to be communicated with the external control type overflow valve group, namely the high-pressure side and the low-pressure side of the external control type overflow valve group are communicated, so that hydraulic impact is reduced, and the vehicle can run stably.
Description
Technical Field
The utility model relates to a vehicle control technical field that traveles especially relates to a vehicle hydraulic control system and vehicle that traveles.
Background
During railway transportation, when the vehicle speed reaches a certain speed or is the vehicle speed expected by the driver, the throttle of the engine is lowered, in the process, the vehicle enters an automatic sliding mode, in the process, the engine can be in an idling speed or a low rotating speed, and the vehicle keeps running at the speed expected by the driver. In the process, the oil consumption of the engine can be saved, and the requirement of the automatic sliding function of the whole vehicle can be met. In the prior art, two modes are generally adopted to control automatic sliding of the vehicle, one mode is a mechanical control system, but the mechanical control system has a problem of complex structure, and the other mode is a hydraulic drive system, but the hydraulic drive system can face impact, and a controller is required to accurately control the displacement of a pump motor to be matched with the vehicle speed.
Therefore, a hydraulic control system for vehicle driving is needed to solve the above technical problems.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide a vehicle hydraulic control system and vehicle of traveling, simple structure can reduce the hydraulic shock when the vehicle switches to the automatic mode of sliding.
To achieve the purpose, the utility model adopts the following technical proposal:
the utility model provides a vehicle hydraulic control system that traveles, including two-way variable pump and two-way variable motor that constitute volume speed governing return circuit, and the engine of drive two-way variable pump pivoted, the hydraulic fluid port that advances of two-way variable pump and two-way variable motor passes through first oil circuit intercommunication, the hydraulic fluid port that reverses of two-way variable pump and two-way variable motor passes through the second oil circuit intercommunication, still include:
the external control type overflow valve bank is connected with the bidirectional variable motor in parallel;
the switch valve bank is arranged between the external control type overflow valve bank and the oil tank;
the first overflow valve is arranged between the switch valve group and the oil tank;
the external control type overflow valve group is provided with a conduction state and an overflow state, when the external control type overflow valve group is in the conduction state, the first oil way is directly communicated with the second oil way, when the external control type overflow valve group is in the overflow state, the first oil way is communicated with the second oil way when the pressure difference between the first oil way and the second oil way exceeds a limit value, and the switch valve group and the first overflow valve are used for controlling the external control type overflow valve group to be switched between the conduction state and the overflow state.
As a preferred technical solution of the above vehicle driving hydraulic control system, the external control type overflow valve group includes a first external control type overflow valve and a second external control type overflow valve, both the first external control type overflow valve and the second external control type overflow valve are connected to the switch valve group, the first external control type overflow valve and the second external control type overflow valve are connected in parallel, an oil inlet of the first external control type overflow valve is communicated with a forward oil port of the bidirectional variable pump, and an oil inlet of the second external control type overflow valve is communicated with a reverse oil port of the bidirectional variable pump.
As a preferable technical solution of the above vehicle driving hydraulic control system, the switch valve group includes a first switch valve and a second switch valve, the first switch valve is disposed between the first externally-controlled overflow valve and the oil tank, the second switch valve is disposed between the second externally-controlled overflow valve and the oil tank, and the first switch valve and the second switch valve are respectively connected to the first overflow valve.
As a preferable technical solution of the above vehicle running hydraulic control system, the switching valve group includes a three-position three-way electromagnetic valve, a port P of the three-position three-way electromagnetic valve is communicated with the first overflow valve, and a port a and a port B of the three-position three-way electromagnetic valve are respectively communicated with the first externally controlled overflow valve and the second externally controlled overflow valve.
As a preferable technical solution of the vehicle running hydraulic control system, a first high-pressure overflow valve is arranged on the first oil path, an oil inlet of the first high-pressure overflow valve is communicated with an oil inlet of the bidirectional variable pump, and the first high-pressure overflow valve is connected in parallel with the first externally-controlled overflow valve.
As a preferable technical scheme of the vehicle running hydraulic control system, a second high-pressure overflow valve is arranged on the second oil path, an oil inlet of the second high-pressure overflow valve is communicated with a reversing oil port of the bidirectional variable pump, and the second high-pressure overflow valve is communicated with the first high-pressure overflow valve.
As a preferable technical solution of the above vehicle driving hydraulic control system, the first switch valve and the second switch valve are both two-position two-way solenoid valves.
As a preferable technical solution of the vehicle travel hydraulic control system, the first externally controlled relief valve and the second externally controlled relief valve are externally controlled pilot relief valves.
As a preferable technical solution of the above vehicle running hydraulic control system, the first high-pressure relief valve and the second high-pressure relief valve are both communicated with a second relief valve, and the second relief valve is communicated with the oil tank.
The utility model also provides a vehicle, including the aforesaid the vehicle hydraulic control system that traveles.
The utility model discloses beneficial effect:
the utility model discloses in increase outer accuse formula overflow valves, ooff valve group and first overflow valve between two-way variable pump and two-way variable motor, when the vehicle switches over to the automatic mode of sliding, the state of adjusting the ooff valve earlier makes two-way variable pump and outer accuse formula overflow valves intercommunication, and the high pressure side and the low pressure side intercommunication of outer accuse formula overflow valves promptly have reduced hydraulic shock then, make the vehicle steadily travel.
Drawings
Fig. 1 is a schematic structural diagram of a vehicle driving hydraulic control system provided by an embodiment of the present invention.
In the figure:
1. a bidirectional variable displacement pump; 2. a bidirectional variable motor; 3. an engine; 4. a first oil passage; 5. a second oil passage; 6. a first externally controlled overflow valve; 7. a second externally controlled overflow valve; 8. a first on-off valve; 9. a second on-off valve; 10. a first overflow valve; 11. a first high-pressure relief valve; 12. a second high-pressure relief valve; 13. a second relief valve.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some of the structures related to the present invention are shown in the drawings, not all of the structures.
In the description of the present invention, unless expressly stated or limited otherwise, the terms "connected," "connected," and "fixed" are to be construed broadly, e.g., as meaning permanently connected, detachably connected, or integral to one another; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present disclosure, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may comprise direct contact between the first and second features, or may comprise contact between the first and second features not directly. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
In the description of the present embodiment, the terms "upper", "lower", "right", etc. are used in an orientation or positional relationship based on that shown in the drawings only for convenience of description and simplicity of operation, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used only for descriptive purposes and are not intended to have a special meaning.
As shown in fig. 1, the present embodiment provides a vehicle driving hydraulic control system, which includes a bidirectional variable pump 1 and a bidirectional variable motor 2 forming a volume speed regulation circuit, an engine 3 driving the bidirectional variable pump 1 to rotate, an external control type overflow valve group, a switch valve group, and a first overflow valve 10. The forward oil port of the bidirectional variable pump 1 is communicated with the forward oil port of the bidirectional variable motor 2 through a first oil path 4, the reverse oil port of the bidirectional variable pump 1 is communicated with the reverse oil port of the bidirectional variable motor 2 through a second oil path 5, and the external control type overflow valve group is connected with the bidirectional variable motor 2 in parallel; the switch valve group is arranged between the external control type overflow valve group and the oil tank, and the first overflow valve 10 is arranged between the switch valve group and the oil tank; the external control type overflow valve group has a conduction state and an overflow state, when the external control type overflow valve group is in the conduction state, the first oil way 4 is directly communicated with the second oil way 5, when the external control type overflow valve group is in the overflow state, the pressure difference between the first oil way 4 and the second oil way 5 is communicated when the pressure difference exceeds a limit value, and the switch valve group and the first overflow valve 10 are used for controlling the external control type overflow valve group to be switched between the conduction state and the overflow state.
In the embodiment, an external control type overflow valve group, a switch valve group and a first overflow valve 10 are additionally arranged between a bidirectional variable pump 1 and a bidirectional variable motor 2, when a vehicle is switched to a normal running mode, the displacements of the bidirectional variable pump 1 and the bidirectional variable motor 2 are adjusted to the displacement corresponding to the current vehicle speed, and then the state of the switch valve group is adjusted to enable the variable pump and the variable motor to be communicated to form a circulation loop; when the vehicle is switched to the automatic sliding mode, the state of the switch valve group is firstly adjusted to enable the bidirectional variable pump 1 to be communicated with the external control type overflow valve group, namely high-pressure oil is communicated with low-pressure oil, so that hydraulic impact is reduced, and the vehicle can run stably.
In this embodiment, preferably, the external control type overflow valve group includes a first external control type overflow valve 6 and a second external control type overflow valve 7, both the first external control type overflow valve 6 and the second external control type overflow valve 7 are connected to the switch valve group, the first external control type overflow valve 6 and the second external control type overflow valve 7 are connected in parallel, an oil inlet of the first external control type overflow valve 6 is communicated with an oil inlet of the bidirectional variable pump 1, and an oil inlet of the second external control type overflow valve 7 is communicated with an oil inlet of the bidirectional variable pump 1. The switch valve group comprises a first switch valve 8 and a second switch valve 9, the first switch valve 8 is arranged between the first external control overflow valve 6 and the oil tank, and the second switch valve 9 is arranged between the second external control overflow valve 7 and the oil tank. The first on-off valve 8 and the second on-off valve 9 are connected to a first relief valve 10, respectively. The opening pressure of the first externally controlled overflow valve 6 and the second externally controlled overflow valve 7 should be the same as the opening pressure of the first overflow valve 10 after the switch valve group is opened, the opening pressure of the first overflow valve 10 in this embodiment is 75bar, and the pressure of the first overflow valve 10 can be set according to field debugging.
A driver opens the first switch valve 8 or the second switch valve 9 according to actual conditions, taking the case that the driver opens the first switch valve 8 as an example, after the first switch valve 8 is opened, the first external control overflow valve 6 communicated with the first switch valve 8 is communicated with the first overflow valve 10, at this time, the signal oil of the first external control overflow valve 6 flows into the oil tank through the first overflow valve 10, the first overflow valve 10 establishes a certain pressure and conducts the certain pressure to the first external control overflow valve 6, so that the high-pressure side and the low-pressure side of the first external control overflow valve 6 are conducted, the hydraulic oil directly enters the first external control overflow valve 6 and flows back to the bidirectional variable pump 1, the oil short circuit of the bidirectional variable motor 2 is realized, the bidirectional variable motor 2 automatically rotates due to inertia, the load is driven to automatically slide, and the energy-saving effect can be achieved.
Preferably, in this embodiment, the first oil path 4 is provided with a first high-pressure overflow valve 11, an oil inlet of the first high-pressure overflow valve 11 is communicated with an oil inlet of the bidirectional variable pump 1, and the first high-pressure overflow valve 11 is connected in parallel with the first externally controlled overflow valve 6. The second oil path 5 is provided with a second high-pressure overflow valve 12, an oil inlet of the second high-pressure overflow valve 12 is communicated with a backward oil port of the bidirectional variable pump 1, and the second high-pressure overflow valve 12 is communicated with the first high-pressure overflow valve 11. The first high-pressure overflow valve 11 and the second high-pressure overflow valve 12 are both communicated with a second overflow valve 13, and the second overflow valve 13 is communicated with an oil tank to overflow oil into the oil tank. In this embodiment, the opening pressures of the first high-pressure overflow valve 11 and the second high-pressure overflow valve 12 are 380bar, and when the oil pressure of the first oil path 4 exceeds the preset value of the first high-pressure overflow valve 11, the oil flows back into the bidirectional variable displacement pump 1 through the first high-pressure overflow valve 11 and the second high-pressure overflow valve 12, so that the hydraulic control system for vehicle running is further protected. When the oil pressure of the second oil path 5 exceeds the preset value of the second high-pressure overflow valve 12, the oil flows back into the bidirectional variable displacement pump 1 through the second high-pressure overflow valve 12 and the first high-pressure overflow valve 11. The opening pressures of the first high-pressure overflow valve 11 and the second high-pressure overflow valve 12 are both smaller than the opening pressures of the first externally controlled overflow valve 6 and the second externally controlled overflow valve 7. It should be noted that the first high-pressure relief valve 11 and the second high-pressure relief valve 12 are integrated as a check valve and a relief valve, and this structure is the prior art and will not be described herein again. When oil needs to be replenished in the bidirectional variable pump 1, the one-way function of the first high-pressure overflow valve 11 or the second high-pressure overflow valve 12 is opened to replenish the oil for the bidirectional variable pump 1.
The first externally controlled overflow valve 6 and the second externally controlled overflow valve 7 are externally controlled pilot overflow valves. The switch valve group is connected with the external control type overflow valve group to realize external control on the external control type overflow valve group, so that the first external control type overflow valve 6 or the second external control type overflow valve 7 can unload pilot oil through the first overflow valve 10, the high-pressure side and the low-pressure side of the first external control type overflow valve 6 or the second external control type overflow valve 7 are communicated, and the first external control type overflow valve 6 or the second external control type overflow valve 7 is communicated with the bidirectional variable pump 1 to form a circulation loop.
The vehicle is generally a vehicle that travels on a track, such as a train, a motor car, a high-speed rail, a tram, and a subway, and the present embodiment further describes the vehicle control system in detail by taking the train as an example.
The train running process has a normal running mode and an automatic sliding mode, wherein the automatic sliding mode is to save energy, when the train speed reaches the expected speed, the rotating speed of the engine 3 is usually reduced, and meanwhile, the displacement of the bidirectional variable pump 1 and the bidirectional variable motor 2 is greatly reduced, so that the oil consumption is saved, and the train enters the automatic sliding mode. However, the displacement of the bidirectional variable pump 1 and the bidirectional variable motor 2 is rapidly decreased, which causes a serious hydraulic shock to the vehicle travel hydraulic control system formed by the engine 3, the bidirectional variable pump 1, and the bidirectional variable motor 2.
For this reason, external control type overflow valve group, switch valve group and first overflow valve 10 have been add to this embodiment, and specifically, above-mentioned first ooff valve 8 and second ooff valve 9 are two-way solenoid valves. The high-pressure oil side and the low-pressure oil side of the first externally controlled overflow valve 6 are communicated when the first switch valve 8 is in an open state, and the high-pressure oil side and the low-pressure oil side of the second externally controlled overflow valve 7 are communicated when the second switch valve 9 is in an open state, so that an automatic sliding mode is realized.
When the train is switched from the automatic sliding mode to the normal running mode, because the bidirectional variable motor 2 and the bidirectional variable motor 2 are in the off state in the automatic sliding mode, the displacement of the variable pump 1 and the displacement of the variable motor 2 can be adjusted to the displacement matched with the current vehicle speed, and then the first switch valve 8 or the second switch valve 9 in the on state is closed. When the train is switched from the normal running mode to the automatic sliding mode, because the oil outlets of the bidirectional variable pump 1 and the bidirectional variable motor 2 are communicated to form a circulation loop in the normal running mode, when a driver wants to enter the automatic sliding mode, the driver can pull back an accelerator operating rod of the engine 1 at the moment, firstly, the first switch valve 8 or the second switch valve 9 is in an open state, so that the oil outlet of the bidirectional variable pump 1 is disconnected with the bidirectional variable motor 2, and then, the displacement of the variable pump and the displacement of the variable motor are both reduced to zero. The control pressure of the first externally controlled overflow valve 6 or the second externally controlled overflow valve 7 is relieved through the first overflow valve 10. At this time, the high-pressure oil flows into the low-pressure side through the first externally controlled relief valve 6 or the second externally controlled relief valve 7, so that the high-pressure side and the low-pressure side are communicated, and thus, the hydraulic power is cut off, so that automatic sliding is realized, and the vehicle does not impact. When the discharge capacities of the bidirectional variable pump 1 and the bidirectional variable motor 2 are adjusted greatly, high-pressure oil and low-pressure oil are already in a communicated state, the pressure of an oil outlet of the bidirectional variable pump 1 is basically equal to the pressure of an oil outlet of the bidirectional variable motor 2, and then hydraulic impact is reduced, so that a train can run stably.
It should be noted that, in other embodiments, the switch valve set may further include a three-position three-way electromagnetic valve, where a port P of the three-position three-way electromagnetic valve is communicated with the first overflow valve 10, and a port a and a port B of the three-position three-way electromagnetic valve are respectively communicated with the first externally controlled overflow valve 6 and the second externally controlled overflow valve 7.
The embodiment also provides a vehicle which comprises the vehicle running hydraulic control system provided by the embodiment.
In addition, the foregoing is only the preferred embodiment of the present invention and the technical principles applied thereto. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, although the present invention has been described in greater detail with reference to the above embodiments, the present invention is not limited to the above embodiments, and may include other equivalent embodiments without departing from the scope of the present invention.
Claims (10)
1. A vehicle running hydraulic control system comprises a bidirectional variable pump (1) and a bidirectional variable motor (2) which form a volume speed regulation loop, and an engine (3) for driving the bidirectional variable pump (1) to rotate, wherein a forward oil port of the bidirectional variable pump (1) is communicated with a forward oil port of the bidirectional variable motor (2) through a first oil path (4), a backward oil port of the bidirectional variable pump (1) is communicated with a backward oil port of the bidirectional variable motor (2) through a second oil path (5), and the vehicle running hydraulic control system is characterized by further comprising:
the external control type overflow valve bank is connected with the bidirectional variable motor (2) in parallel;
the switch valve bank is arranged between the external control type overflow valve bank and the oil tank;
the first overflow valve (10) is arranged between the switch valve group and the oil tank;
the external control type overflow valve group is provided with a conduction state and an overflow state, when the external control type overflow valve group is in the conduction state, the first oil way (4) is directly communicated with the second oil way (5), when the external control type overflow valve group is in the overflow state, the first oil way (4) is communicated with the second oil way (5) when the pressure difference between the first oil way (4) and the second oil way (5) exceeds a limit value, and the switch valve group and the first overflow valve (10) are used for controlling the external control type overflow valve group to be switched between the conduction state and the overflow state.
2. The vehicle running hydraulic control system according to claim 1, wherein the external control type overflow valve group comprises a first external control type overflow valve (6) and a second external control type overflow valve (7), the first external control type overflow valve (6) and the second external control type overflow valve (7) are both connected with the switch valve group, the first external control type overflow valve (6) and the second external control type overflow valve (7) are connected in parallel, an oil inlet of the first external control type overflow valve (6) is communicated with a forward oil port of the bidirectional variable pump (1), and an oil inlet of the second external control type overflow valve (7) is communicated with a reverse oil port of the bidirectional variable pump (1).
3. The vehicle running hydraulic control system according to claim 2, wherein the switch valve group includes a first switch valve (8) and a second switch valve (9), the first switch valve (8) is disposed between the first externally controlled overflow valve (6) and the tank, the second switch valve (9) is disposed between the second externally controlled overflow valve (7) and the tank, and the first switch valve (8) and the second switch valve (9) are respectively connected to the first overflow valve (10).
4. The vehicle running hydraulic control system according to claim 2, wherein the switch valve group comprises a three-position three-way solenoid valve, a port P of the three-position three-way solenoid valve is communicated with the first overflow valve (10), and a port a and a port B of the three-position three-way solenoid valve are respectively communicated with the first externally controlled overflow valve (6) and the second externally controlled overflow valve (7).
5. The vehicle running hydraulic control system according to claim 2, wherein a first high-pressure overflow valve (11) is arranged on the first oil path (4), an oil inlet of the first high-pressure overflow valve (11) is communicated with an oil inlet of the bidirectional variable pump (1), and the first high-pressure overflow valve (11) is connected in parallel with the first externally-controlled overflow valve (6).
6. The vehicle running hydraulic control system according to claim 5, wherein a second high-pressure overflow valve (12) is arranged on the second oil path (5), an oil inlet of the second high-pressure overflow valve (12) is communicated with a reversing oil port of the bidirectional variable pump (1), and the second high-pressure overflow valve (12) is communicated with the first high-pressure overflow valve (11).
7. The vehicle running hydraulic control system according to claim 3, wherein the first switch valve (8) and the second switch valve (9) are both two-position two-way solenoid valves.
8. The vehicle-running hydraulic control system according to claim 2, wherein the first externally controlled relief valve (6) and the second externally controlled relief valve (7) are externally controlled pilot relief valves.
9. The vehicle running hydraulic control system according to claim 6, wherein the first high-pressure relief valve (11) and the second high-pressure relief valve (12) are both communicated with a second relief valve (13), and the second relief valve (13) is communicated with the tank.
10. A vehicle characterized by comprising the vehicle running hydraulic control system according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921676182.9U CN210859382U (en) | 2019-09-30 | 2019-09-30 | Vehicle running hydraulic control system and vehicle |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921676182.9U CN210859382U (en) | 2019-09-30 | 2019-09-30 | Vehicle running hydraulic control system and vehicle |
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| CN210859382U true CN210859382U (en) | 2020-06-26 |
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| CN201921676182.9U Active CN210859382U (en) | 2019-09-30 | 2019-09-30 | Vehicle running hydraulic control system and vehicle |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113187782A (en) * | 2021-05-07 | 2021-07-30 | 潍柴动力股份有限公司 | Control method, device and equipment of closed hydraulic system and storage medium |
| CN113236616A (en) * | 2021-05-26 | 2021-08-10 | 广州嘉泰液压机电有限公司 | Proportional variable pump control device and control method thereof |
-
2019
- 2019-09-30 CN CN201921676182.9U patent/CN210859382U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113187782A (en) * | 2021-05-07 | 2021-07-30 | 潍柴动力股份有限公司 | Control method, device and equipment of closed hydraulic system and storage medium |
| CN113236616A (en) * | 2021-05-26 | 2021-08-10 | 广州嘉泰液压机电有限公司 | Proportional variable pump control device and control method thereof |
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