Rack rail vehicle power switching hydraulic system and rack rail vehicle

Abstract

The invention provides a rack rail vehicle power switching hydraulic system and a rack rail vehicle. The rack rail vehicle power switching hydraulic system comprises a main pump, a gear drive motor, a wheel drive motor, a switching valve set and a functional valve set. The switching valve group is connected among the main pump, the gear drive motor and the wheel drive motor; the switching valve group has a tooth driving state in which the tooth driving motor and the main pump are connected in series and a wheel driving state in which the wheel driving motor and the main pump are connected in series; a first free wheel valve group is connected between the two oil ports of the gear drive motor, and a second free wheel valve group is connected between the two oil ports of the wheel drive motor. According to the rack rail vehicle power switching hydraulic system, the wheel drive motors are arranged, so that the rack rail vehicle can drive the wheels to run through the wheel drive motors under the non-gradient condition, adhesion driving of the wheels of the rack rail vehicle is achieved, and the requirement for rapid and efficient running of the rack rail vehicle on a straight rail is met. And meanwhile, due to the arrangement of the switching valve group and the functional valve group, the rack rail vehicle can be switched between two modes.

Description

Technical Field

[0001] The present invention relates to the technical field of rack rail vehicles, and in particular to a rack rail vehicle power switching hydraulic system. The present invention also relates to a rack rail vehicle provided with the rack rail vehicle power switching hydraulic system. Background Art

[0002] As a special rail transportation tool, rack rail cars are widely used in the mining industry because of their unique gear drive system, which enables them to achieve efficient and stable driving on complex terrain and steep slopes, and their ability to carry out efficient transportation under complex terrain and slope conditions.

[0003] At present, rack rail vehicles generally adopt a single drive mode of gear drive, which mainly uses the meshing of gears and racks on the track to drive the rack rail vehicle to climb slopes and travel on complex terrain. However, on straight sections and without slope conditions, existing rack rail vehicles only use the gear drive mode to travel, which makes it difficult to travel at high speed on straight tracks, and also cannot travel on non-rack sections. Summary of the invention

[0004] In view of this, the present invention aims to provide a power switching hydraulic system for a rack rail vehicle, which can realize wheel adhesion drive of the rack rail vehicle and realize switching of the rack rail vehicle between two driving modes.

[0005] To achieve the above object, the technical solution of the present invention is achieved as follows:

[0006] A power switching hydraulic system for a rack rail vehicle, comprising a main pump, a gear drive motor, a wheel drive motor, a switching valve group, and a functional valve group;

[0007] The gear drive motor is transmission connected to the gear, and the wheel drive motor is transmission connected to the wheel;

[0008] The switching valve group is connected between the main pump and the gear drive motor and the wheel drive motor;

[0009] The switching valve group has a gear drive state in which the gear drive motor and the main pump are connected in series, and a wheel drive state in which the wheel drive motor and the main pump are connected in series;

[0010] A first freewheel valve group is connected between the two oil ports of the gear drive motor, and a second freewheel valve group is connected between the two oil ports of the wheel drive motor;

[0011] The functional valve group has a first state for controlling the second freewheel valve group to conduct the two oil ports of the wheel drive motor, and a second state for controlling the first freewheel valve group to conduct the two oil ports of the gear drive motor.

[0012] Furthermore, it also includes a master control valve and a first auxiliary pump; the oil inlet of the master control valve is connected to the first auxiliary pump, and the oil return port of the master control valve is connected to the oil tank; the first auxiliary pump can provide control oil pressure to the switching valve group and the functional valve group through the working oil port of the master control valve, so as to drive the switching valve group to switch between the gear drive state and the wheel drive state, and drive the functional valve group to switch between the first state and the second state.

[0013] Further, the switching valve group includes a first gear-driven cartridge valve, a second gear-driven cartridge valve, a first wheel-driven cartridge valve, a second wheel-driven cartridge valve and a first reversing valve; an oil port of the main pump is connected to the first oil port of the first gear-driven cartridge valve and the first wheel-driven cartridge valve, and another oil port of the main pump is connected to the first oil port of the second gear-driven cartridge valve and the second wheel-driven cartridge valve; the second oil ports of the first gear-driven cartridge valve and the second gear-driven cartridge valve are respectively connected to the two oil ports of the gear-driven motor, and the first wheel-driven cartridge valve and the second wheel-driven cartridge valve are connected to the first oil port of the first gear-driven cartridge valve and the second wheel-driven cartridge valve. The second oil port of the wheel drive cartridge valve is respectively connected to the two oil ports of the wheel drive motor; the oil inlet of the first reversing valve is connected to one of the two oil ports of the main pump, and the oil return port of the first reversing valve is connected to the oil tank; the first working oil port of the first reversing valve is connected to the control oil ports of the first gear drive cartridge valve and the second gear drive cartridge valve, and the second working oil port of the first reversing valve is connected to the control oil ports of the first wheel drive cartridge valve and the second wheel drive cartridge valve; the control oil port of the first reversing valve is connected to the working oil port of the master control valve.

[0014] Furthermore, the functional valve group includes a second reversing valve; the oil inlet of the second reversing valve is connected to the first auxiliary pump, and the oil return port of the second reversing valve is connected to the oil tank; the first working oil port of the second reversing valve can input oil pressure to the second free-wheel valve group; the second working oil port of the second reversing valve can input oil pressure to the first free-wheel valve group; the control oil port of the second reversing valve is connected to the working oil port of the master control valve.

[0015] Furthermore, the first free-wheel valve group includes a first stop valve, and the second free-wheel valve group includes a second stop valve; the control oil port of the first stop valve is connected to the second working oil port of the second reversing valve, and the control oil port of the second stop valve is connected to the first working oil port of the second reversing valve; when the second reversing valve provides oil pressure to the control oil ports of the first stop valve and the second stop valve, the first stop valve can conduct the two oil ports of the gear drive motor, and the second stop valve can conduct the two oil ports of the wheel drive motor.

[0016] Furthermore, the second stop valves are configured as two connected in series, and an oil return oil circuit connected to the oil tank is provided between the two second stop valves; and / or, the two oil ports of the gear drive motor are connected to the second auxiliary pump through an oil replenishment circuit.

[0017] Furthermore, the functional valve group also includes a third reversing valve; the oil inlet of the third reversing valve is connected to the first auxiliary pump, and the oil return port of the third reversing valve is connected to the oil tank; the first working port of the third reversing valve is connected to the housing oil discharge port of the wheel drive motor through two branches, and one of the branches is connected in series with a pressure reducing valve, and the other branch is provided with a one-way valve; the control oil port of the third reversing valve is connected to the working oil port of the master control valve.

[0018] Furthermore, the gear-driven motor is a variable motor, and the two cavities of the single-piston variable cylinder of the gear-driven motor are connected to the variable valve group through the first variable oil circuit and the second variable oil circuit respectively; the variable valve group includes a variable control valve, the oil inlet of the variable control valve is connected to the auxiliary oil circuit, the oil return port of the variable control valve is connected to the oil tank, and the working oil port of the variable control valve is connected to the second variable oil circuit; the first variable oil circuit can be connected to any oil port of the gear-driven motor, and connected to the auxiliary oil circuit; the first control oil port of the variable control valve is connected to the second working oil port of the third reversing valve, and the second control oil port of the variable control valve is connected to the first variable oil circuit.

[0019] Furthermore, it also includes an auxiliary valve group; the auxiliary valve group includes an accumulator, a fourth reversing valve and two brake oil circuits; the two brake oil circuits are respectively connected to the gear-driven brake cylinder and the wheel-driven brake cylinder; the oil inlet of the fourth reversing valve is connected to the accumulator, and the two working oil ports of the fourth reversing valve are respectively connected to the two brake oil circuits.

[0020] Compared with the prior art, the present invention has the following advantages:

[0021] The power switching hydraulic system of the rack vehicle of the present invention, by setting a wheel drive motor, enables the rack vehicle to drive the wheels to travel under non-slope conditions through the wheel drive motor, realizes wheel adhesion drive of the rack vehicle, and satisfies the requirement of fast and efficient travel of the rack vehicle on a straight track. At the same time, the setting of the switching valve group and the functional valve group can realize the switching of the rack vehicle between the gear drive mode and the wheel adhesion drive mode, so that the rack vehicle can travel on complex terrain and steep slopes through gear drive, and can also meet the characteristics of fast and efficient travel of the rack vehicle on a straight track through wheel adhesion drive.

[0022] Another object of the present invention is to provide a rack rail vehicle, in which the rack rail vehicle power switching hydraulic system as described above is provided.

[0023] The rack rail vehicle and / or the rack rail vehicle power switching hydraulic system described in the present invention have the same technical effects as those of the prior art, and will not be described in detail herein. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The accompanying drawings constituting a part of the present invention are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the accompanying drawings:

[0025] Figure 1 It is a schematic diagram of the overall structure of the power switching hydraulic system of a rack rail vehicle according to an embodiment of the present invention;

[0026] Figure 2 It is a schematic diagram of the connection between the switching valve group and the gear-driven motor in the gear-driven state according to an embodiment of the present invention;

[0027] Figure 3 A schematic diagram of the connection between the switching valve group and the wheel drive motor in the wheel drive state according to an embodiment of the present invention;

[0028] Figure 4 It is a schematic diagram of the connection between the functional valve group and each free wheel valve group in the first state according to an embodiment of the present invention;

[0029] Figure 5 It is a schematic diagram of the connection between the functional valve group and each free wheel valve group in the second state according to an embodiment of the present invention;

[0030] Figure 6 It is a schematic diagram of the connection between the functional valve group according to an embodiment of the present invention and the wheel drive motor and the gear drive motor in the first state;

[0031] Figure 7 It is a schematic diagram of the connection between the functional valve group according to an embodiment of the present invention and the wheel drive motor and the gear drive motor in the second state;

[0032] Figure 8 A schematic diagram of the connection between the auxiliary valve group and each brake cylinder according to an embodiment of the present invention;

[0033] Description of reference numerals:

[0034] 1. Main pump;

[0035] 2. Gear-driven motor; 201. First freewheel valve group; 2011. First stop valve; 202. Single-piston variable cylinder; 203. Variable valve group; 2031. Variable control valve; 2032. Two-position six-way hydraulic control valve; 204. Gear-driven brake cylinder;

[0036] 3. Wheel drive motor; 301. Second free wheel valve group; 3011. Second stop valve; 302. Wheel drive brake cylinder;

[0037] 4. Switching valve group; 401. First gear-driven cartridge valve; 402. Second gear-driven cartridge valve; 403. First wheel-driven cartridge valve; 404. Second wheel-driven cartridge valve; 405. First reversing valve; 406. Shuttle valve; 407. Two-way ball valve;

[0038] 5. Functional valve group; 501. Second reversing valve; 502. Third reversing valve; 503. Pressure reducing valve; 504. Check valve; 505. Main pump control pressure valve;

[0039] 6. Master control valve;

[0040] 7. First auxiliary pump;

[0041] 8. Flow diversion and collection valve;

[0042] 9. Auxiliary valve group; 901. Accumulator; 902. Fourth reversing valve; 903. Second auxiliary pump. DETAILED DESCRIPTION

[0043] It should be noted that, in the absence of conflict, the embodiments of the present invention and the features in the embodiments may be combined with each other.

[0044] In the following description, specific details such as specific system structures, technologies, etc. are provided for the purpose of illustration rather than limitation, so as to provide a thorough understanding of the embodiments of the present application. However, it should be clear to those skilled in the art that the present application may also be implemented in other embodiments without these specific details. In other cases, detailed descriptions of well-known systems, devices, circuits, and methods are omitted to prevent unnecessary details from obstructing the description of the present application.

[0045] In the description of the present invention, it should be noted that if there are terms indicating orientation or positional relationship such as "upper", "lower", "inner", "outer", etc., they are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, if there are terms such as "first", "second", etc., they are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0046] In addition, in the description of the present invention, unless otherwise clearly defined, the terms "installed", "connected", "connection" and "connector" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood in combination with specific circumstances.

[0047] The present invention will be described in detail below with reference to the accompanying drawings and in conjunction with embodiments.

[0048] Embodiment 1

[0049] This embodiment relates to a power switching hydraulic system for a rack rail vehicle, such as Figure 1 As shown, the overall structure includes a main pump 1, a gear drive motor 2, a wheel drive motor 3, a switching valve group 4, and a functional valve group 5. Among them, the gear drive motor 2 is connected to the gear of the rack vehicle, and the wheel drive motor 3 is connected to the wheel. The switching valve group 4 is connected between the main pump 1 and the gear drive motor 2 and the wheel drive motor 3, and the switching valve group 4 has a gear drive state in which the gear drive motor 2 and the main pump 1 are connected in series, and a wheel drive state in which the wheel drive motor 3 and the main pump 1 are connected in series.

[0050] A first freewheel valve group 201 is connected between the two oil ports of the gear drive motor 2, and a second freewheel valve group 301 is connected between the two oil ports of the wheel drive motor 3. The functional valve group 5 has a first state of controlling the second freewheel valve group 301 to conduct the two oil ports of the wheel drive motor 3, and a second state of controlling the first freewheel valve group 201 to conduct the two oil ports of the gear drive motor 2. When the switching valve group 4 is in the gear drive state, the main pump 1 can drive the gear drive motor 2 to work, and the functional valve group 5 can conduct the two oil ports of the wheel drive motor 3 in the first state to put the wheel drive motor 3 in a freewheel state, at which time the rack rail vehicle is in a gear drive mode. When the switching valve group 4 is in the wheel drive state, the main pump 1 can drive the wheel drive motor 3 to work, and the functional valve group 5 can conduct the two oil ports of the gear drive motor 2 in the second state to put the gear drive motor 2 in a freewheel state, at which time the rack rail vehicle is in a vehicle adhesion drive mode.

[0051] As described above, by setting the wheel drive motor, the rack vehicle can drive the wheels to travel under the condition of no slope through the wheel drive motor, so as to realize the wheel adhesion drive of the rack vehicle, so as to meet the requirements of fast and efficient travel of the rack vehicle on a straight track. At the same time, the setting of the switching valve group 4 and the functional valve group 5 can realize the switching of the rack vehicle between the gear drive mode and the wheel adhesion drive mode, so that the rack vehicle can travel on complex terrain and steep slopes through gear drive, and can also meet the characteristics of fast and efficient travel of the rack vehicle on a straight track through wheel adhesion drive.

[0052] Based on the above overall introduction, specifically, the rack rail vehicle has multiple wheels and gears for traveling, so the gear drive motors 2 and wheel drive motors 3 in this embodiment are multiple and arranged in parallel. A flow divider and collector valve 8 is also provided between the first wheel drive cartridge valve 403 and each wheel drive motor 3 to ensure that the main pump 1 supplies the same flow to each wheel drive motor 3 and ensure that each wheel drive motor 3 works synchronously.

[0053] The rack vehicle power switching hydraulic system of this embodiment needs to control the switching valve group 4 to be in the gear drive state and control the functional valve group 5 to be in the first state in the gear drive mode. In the wheel adhesion mode, it is necessary to control the switching valve group 4 to be in the wheel drive state and control the functional valve group 5 to be in the second state. In order to facilitate the control of the switching valve group 4 and the functional valve group 5, this embodiment also includes a master control valve 6 and a first auxiliary pump 7. Among them, the oil inlet of the master control valve 6 is connected to the first auxiliary pump 7, and the oil return port of the master control valve 6 is connected to the oil tank. The first auxiliary pump 7 can provide control oil pressure to the switching valve group 4 and the functional valve group 5 through the working oil port of the master control valve 6, so as to drive the switching valve group 4 to switch between the gear drive state and the wheel drive state, and drive the functional valve group 5 to switch between the first state and the second state.

[0054] The switching valve group 4 and the functional valve group 5 are controlled by the master control valve 6. The switching valve group 4 is used as a central controller. The switching of the states of the switching valve group 4 and the functional valve group 5 can be controlled simultaneously to ensure the synchronization of the state switching process of the switching valve group 4 and the functional valve group 5, so as to increase the speed of the driving mode switching and ensure the stability of the driving mode switching process.

[0055] In specific implementation, the master control valve 6 of this embodiment is a two-position three-way solenoid valve, so that the operation of the master control valve 6 can be controlled by the electrical control component of the rack rail vehicle cab. When the master control valve 6 is not energized, the master control valve 6 conducts the working oil port and the oil return port, so that the control hydraulic oil used to control the switching valve group 4 and the functional valve group 5 can flow back to the oil tank, so that the switching valve group 4 is in the gear drive state, and the functional valve group 5 is in the first state. When the master control valve 6 is energized, the master control valve 6 conducts the oil inlet and the working oil port, so that the first auxiliary pump 7 provides control oil pressure to the switching valve group 4 and the functional valve group 5, so that the switching valve group 4 is in the wheel drive state, and the functional valve group 5 is in the second state.

[0056] On this basis, combined with Figure 2 , Figure 3 As shown, the switching valve group 4 of this embodiment includes a first gear-driven cartridge valve 401, a second gear-driven cartridge valve 402, a first wheel-driven cartridge valve 403, a second wheel-driven cartridge valve 404 and a first reversing valve 405, and the first reversing valve 405 is a two-position four-way hydraulically controlled reversing valve.

[0057] Among them, one oil port of the main pump 1 is connected to the first oil port of the first gear drive cartridge valve 401 and the first wheel drive cartridge valve 403, and the other oil port of the main pump 1 is connected to the first oil port of the second gear drive cartridge valve 402 and the second wheel drive cartridge valve 404. The second oil ports of the first gear drive cartridge valve 401 and the second gear drive cartridge valve 402 are respectively connected to the two oil ports of the gear drive motor 2, and the second oil ports of the first wheel drive cartridge valve 403 and the second wheel drive cartridge valve 404 are respectively connected to the two oil ports of the wheel drive motor 3. It can be understood that the first gear drive cartridge valve 401 and the second gear drive cartridge valve 402 are connected between the main pump 1 and the gear drive motor 2, and the first wheel drive cartridge valve 403 and the second wheel drive cartridge valve 404 are connected between the main pump 1 and the wheel drive motor 3. The switching valve group 4 is connected to the gear drive motor 2 through the AG and BG oil ports, and is connected to the wheel drive motor 3 through the AW and BW oil ports.

[0058] The oil inlet of the first reversing valve 405 is connected to one of the two oil ports of the main pump 1, and the oil return port of the first reversing valve 405 is connected to the oil tank. The first working oil port of the first reversing valve 405 is connected to the control oil ports of the first gear drive cartridge valve 401 and the second gear drive cartridge valve 402, and the second working oil port of the first reversing valve 405 is connected to the control oil ports of the first wheel drive cartridge valve 403 and the second wheel drive cartridge valve 404.

[0059] When the switching valve group 4 is in the gear drive state, Figure 2 As shown, the oil inlet of the first reversing valve 405 and the first working oil port are connected, and the oil return port of the first reversing valve 405 and the second working oil port are connected. At this time, the hydraulic oil output by the main pump 1 can enter the cavity of each cartridge valve, and the hydraulic oil output by the main pump 1 enters the control oil ports of the first wheel drive cartridge valve 403 and the second wheel drive cartridge valve 404 through the first reversing valve 405, so that the two of them block the connection between the main pump 1 and the wheel drive motor 3. The first gear drive cartridge valve 401 and the second gear drive cartridge valve 402 conduct the main pump 1 and the gear drive motor 2.

[0060] Similarly, when the switching valve group 4 is in the wheel drive state, Figure 3 As shown, the hydraulic oil output by the main pump 1 enters the control oil ports of the first gear drive cartridge valve 401 and the second gear drive cartridge valve 402 through the first reversing valve 405, so that the two of them block the connection between the main pump 1 and the gear drive motor 2, thereby realizing the switching of the switching valve group 4 between the gear drive mode and the wheel drive mode. At the same time, the control oil port of the first reversing valve 405 is connected to the working oil port of the master control valve 6, so that the master control valve 6 can control the switching valve group 4 by controlling the action of the first reversing valve 405.

[0061] In specific implementation, the two oil ports of the main pump 1 of this embodiment are connected to the A and B oil ports of the switching valve group 4, and the main pump 1 can change the flow direction of the hydraulic oil at the A and B oil ports by the forward and reverse rotation of its own inclined plate, thereby controlling the forward and reverse rotation of the gear drive motor 2 or the wheel drive motor 3. In addition, the two oil ports of the main pump 1 are connected to the oil inlet of the first reversing valve 405 through a shuttle valve 406. The shuttle valve 406 can introduce the high-pressure side pressure signal of the main pump 1 into the spring control chamber of each corresponding cartridge valve through the first reversing valve 405, and use its own pilot area ratio to ensure that the corresponding cartridge valves can be effectively blocked. In addition, a two-way ball valve 407 is also connected between the two oil ports of the main pump 1 of this embodiment. The two-way ball valve 407 can connect the two oil ports of the main pump 1 to meet the trailer working conditions in emergency situations. As a specific implementation form, such as Figure 4 , Figure 5 As shown, the functional valve group 5 of this embodiment includes a second reversing valve 501. The second reversing valve 501 is a two-position four-way hydraulically controlled reversing valve.

[0062] The oil inlet of the second reversing valve 501 is connected to the first auxiliary pump 7, and the oil return port of the second reversing valve 501 is connected to the oil tank. The first working oil port of the second reversing valve 501 can input oil pressure to the second freewheel valve group 301. The second working oil port of the second reversing valve 501 can input oil pressure to the first freewheel valve group 201. And the control oil port of the second reversing valve 501 is connected to the working oil port of the master control valve 6.

[0063] Through the setting of the second reversing valve 501, when the main control valve 6 is not energized and the second reversing valve 501 is in the initial state, the second reversing valve 501 connects the oil inlet and the first working oil port to provide control oil pressure to the second freewheel valve group 301. When the main control valve 6 is energized and the second reversing valve 501 is actuated, the second reversing valve 501 connects the oil inlet and the second working oil port to provide control oil pressure to the first freewheel valve group 201. The second reversing valve 501 can realize the switching of the freewheel working conditions of the gear drive motor 2 and the wheel drive motor 3. At the same time, since the main control valve 6 can control the action of the second reversing valve 501, the synchronization of the state switching of the switching valve group 4 and the functional valve group 5 is guaranteed.

[0064] Specifically, the first freewheel valve group 201 of this embodiment includes a first stop valve 2011, and the second freewheel valve group 301 includes a second stop valve 3011. Each stop valve is a two-position two-way hydraulic control valve. The control oil port of the first stop valve 2011 is connected to the second working oil port of the second reversing valve 501, and the control oil port of the second stop valve 3011 is connected to the first working oil port of the second reversing valve 501. When the second reversing valve 501 provides oil pressure to the control oil ports of the first stop valve 2011 and the second stop valve 3011, the first stop valve 2011 can conduct the two oil ports of the gear drive motor 2, and the second stop valve 3011 can conduct the two oil ports of the wheel drive motor 3. Therefore, the second reversing valve 501 can provide oil pressure to the control oil ports of the first stop valve 2011 and the second stop valve 3011 respectively, so that the gear drive motor 2 or the wheel drive motor 3 is in a freewheel working state of free rotation.

[0065] Further, such as Figure 6 , Figure 7 As shown, the wheel drive motor 3 of this embodiment can adopt a radial piston hydraulic motor. When the radial piston hydraulic motor is in a free wheel working state, in addition to connecting its two oil ports, the two oil ports also need to be connected to the oil tank. Therefore, the second stop valve 3011 of this embodiment is configured as two connected in series, and a return oil circuit connected to the oil tank is provided between the two second stop valves 3011. When the two second stop valves 3011 are actuated at the same time, the two oil ports of the wheel drive motor 3 can be connected and connected to the oil tank.

[0066] In addition, the gear-driven motor 2 of this embodiment can adopt an axial piston hydraulic motor, and the first freewheel valve group 201 can conduct the two oil ports of the gear-driven motor 2. The two oil ports of the gear-driven motor 2 are connected to the second auxiliary pump 903 through the oil replenishment oil circuit, and the second auxiliary pump 903 is connected to the Pbo oil port of the first freewheel valve group 201 through the oil replenishment oil circuit to replenish oil to the gear-driven motor 2 to avoid cavitation when the gear-driven motor 2 is idling under the freewheel working condition. In specific implementation, an oil replenishment check valve is provided between the Pbo oil port and the two oil ports of the gear-driven motor 2.

[0067] In addition, when the wheel drive motor 3 using a radial piston hydraulic motor is in a free wheel condition, it is also necessary to control the plunger in the wheel drive motor 3 to retract to prevent the plunger from contacting the cam during the idling of the wheel drive motor 3. To this end, as a specific implementation form, the functional valve group 5 of this embodiment also includes a third reversing valve 502. The oil inlet of the third reversing valve 502 is connected to the first auxiliary pump 7, and the oil return port of the third reversing valve 502 is connected to the oil tank. The first working port of the third reversing valve 502 is connected to the housing oil unloading port of the wheel drive motor 3 through two branches, and one branch is connected in series with a pressure reducing valve 503, and the other branch is provided with a one-way valve 504. The control oil port of the third reversing valve 502 is connected to the working oil port of the master control valve 6.

[0068] By setting the third reversing valve 502, when the master control valve 6 is powered off and the third reversing valve 502 is in the initial state, Figure 6 As shown, the third reversing valve 502 connects the oil inlet and the first working oil port, so that the control hydraulic oil output by the first auxiliary pump 7 is output to the housing oil discharge port through the pressure reducing valve 503 to drive the plunger to retract. After the plunger retracts to the position, the oil pressure at the first working oil port rises until the oil pressure reaches the preset value, and then the pressure reducing valve 503 closes the first working oil port.

[0069] When the master control valve 6 is energized to activate the third reversing valve 502, Figure 7 As shown, the wheel drive motor 3 is released from the freewheeling state, at which time the third reversing valve 502 is connected to the oil return port and the first working oil port, and the hydraulic oil in the housing oil discharge port can flow back to the oil tank through the one-way valve 504 and the first working oil port. Therefore, when the master control valve 6 controls the state switching of the functional valve group 5, the third reversing valve 502 can control the plunger of the wheel drive motor 3 to retract, so as to ensure that the wheel drive motor 3 can be in the freewheeling state when the functional valve group 5 is in the first state.

[0070] At the same time, the gear-driven motor 2 of this embodiment is a variable motor, which adjusts the motor displacement by moving the variable rod piston. The two cavities of the single-piston variable cylinder 202 of the gear-driven motor 2 are connected to the variable valve group 203 through the first variable oil circuit and the second variable oil circuit respectively.

[0071] The variable valve group 203 includes a variable control valve 2031, the oil inlet of the variable control valve 2031 is connected to the auxiliary oil circuit, and the auxiliary oil circuit can provide oil pressure to the oil inlet of the variable control valve 2031. The return oil port of the variable control valve 2031 is connected to the oil tank, and the working oil port of the variable control valve 2031 is connected to the second variable oil circuit. The first variable oil circuit can be connected to any oil port of the gear drive motor 2, and the auxiliary oil circuit. The first control oil port of the variable control valve 2031 is connected to the second working oil port of the third reversing valve 502, and the second control oil port of the variable control valve 2031 is connected to the first variable oil circuit.

[0072] When the master control valve 6 controls the switching valve group 4 to be in the gear drive state and the functional valve group 5 is in the first state, the hydraulic oil from the main pump 1 and the auxiliary oil circuit flows to the second control oil port of the variable control valve 2031 to keep the variable control valve 2031 in the initial state. At the same time, the hydraulic oil from the main pump 1 and the auxiliary oil circuit enters the upper cavity of the single-piston variable cylinder 202 through the first variable oil circuit, driving the piston of the single-piston variable cylinder 202 to move and put the gear drive motor 2 in the maximum displacement state.

[0073] When the master control valve 6 controls the switching valve group 4 to be in the wheel drive state and the functional valve group 5 is in the second state, the third reversing valve 502 can conduct the oil inlet and the second working oil port, so that the first auxiliary pump 7 can output oil pressure to the first control oil port of the variable control valve 2031. At the same time, since the two oil ports of the gear drive motor 2 are connected, only the auxiliary oil circuit outputs oil pressure to the second control oil port of the variable control valve 2031, and the oil pressure is much smaller than the oil pressure at the first control oil port of the variable control valve 2031. Therefore, the variable control valve 2031 is actuated to connect the oil inlet and the working oil port, and the auxiliary oil circuit can be connected to the two cavities of the single-piston variable cylinder 202 at the same time, so that the single-piston variable cylinder 202 is in a differential connection state.

[0074] Since the area of ​​the piston ring in the upper cavity of the single-piston variable cylinder 202 is smaller than the area of ​​the piston in the lower cavity of the single-piston variable cylinder 202, when the auxiliary oil circuit outputs oil pressure to the two cavities of the single-piston variable cylinder 202, the pressure applied to the upper cavity is smaller than that of the lower cavity, causing the piston of the single-piston variable cylinder 202 to move upward, so that the gear-driven motor 2 is in the minimum displacement state, avoiding the gear-driven motor 2 from causing resistance to the locomotive's travel under the free-wheel condition, and avoiding heat or cavitation caused by the flow of hydraulic oil, thereby protecting the gear-driven motor 2.

[0075] Therefore, through the setting of the variable valve group 203, the main control valve 6 can control the variable control valve 2031 through the third reversing valve 502. In the wheel drive state, the variable control valve 2031 can put the gear drive motor 2 in the minimum displacement state, thereby protecting the gear drive motor 2 in the free wheel condition.

[0076] In specific implementation, the main pump 1 controls the forward and reverse rotation of the gear-driven motor 2 by changing the flow direction of the hydraulic oil at the A and B oil ports. The A1 oil port of the gear-driven motor 2 is connected to the A oil port of the main pump 1, and the B1 oil port is connected to the B oil port. In this embodiment, the function valve group 5 is provided with a main pump variable cylinder pressure on-off valve 505, and the variable valve group 203 is provided with a two-position six-way hydraulic control valve 2032. When the main pump 1 rotates forward or reverse, it can output control oil pressure to the X1i oil port or the X2i oil port of the main pump variable cylinder pressure on-off valve 505.

[0077] Specifically, taking the main pump 1 supplying oil to the A oil port and returning oil from the B oil port as the main pump 1 forward rotation as an example, when the main pump 1 is forward rotating, the main pump 1 outputs the control oil pressure to the X1i oil port, and when the main pump 1 is reverse rotating, the main pump 1 outputs the control oil pressure to the X2i oil port. The control oil port of the main pump variable cylinder pressure on-off valve 505 is connected to the working oil port of the master control valve 6.

[0078] The X1o oil port of the main pump variable cylinder pressure on-off valve 505 is connected to the X1 oil port of the variable valve group 203, and the X2o oil port is connected to the X2 oil port of the variable valve group 203. That is, the a2 oil port of the two-position six-way hydraulic control valve 2032 is connected to the X1o oil port and the b2 oil port of the two-position six-way hydraulic control valve 2032 is connected to the first control oil port and the X2o oil port, and at the same time, the a1 oil port of the two-position six-way hydraulic control valve 2032 is connected to the A1 oil port, the b1 oil port of the two-position six-way hydraulic control valve 2032 is connected to the B1 oil port, the c oil port of the two-position six-way hydraulic control valve 2032 is connected to the oil inlet of the variable control valve 2031, and the c oil port of the two-position six-way hydraulic control valve 2032 is connected to the first control oil port of the variable control valve 2031. And a one-way valve is connected between A1 and a1, and between B1 and b1 to prevent the hydraulic oil from flowing from a1 to A1, and from b1 to B1.

[0079] Therefore, in the gear drive state, the main pump variable cylinder pressure on-off valve 505 is in the initial state. When the oil pressure on the main pump A1 side is higher, the main pump variable cylinder outputs control oil pressure to a2 and the first control oil port, so that the two-position six-way hydraulic control valve 2032 connects A1 and c oil ports, so that the high-pressure side of the main pump 1 drives the single-piston variable cylinder 202 to operate and the gear drive motor 2 changes variable.

[0080] When the oil pressure on the main pump B1 side is higher, the main pump variable cylinder outputs control oil pressure to b2 and the first control oil port, so that the two-position six-way hydraulic control valve 2032 connects B1 and c oil ports, and continues to make the high-pressure side of the main pump 1 drive the single-piston variable cylinder 202 to operate and make the gear drive motor 2 variable.

[0081] In the wheel drive state, the first auxiliary pump 7 can output oil pressure to the control oil port of the main pump variable cylinder pressure on-off valve 505, so that the main pump variable cylinder pressure on-off valve 505 is actuated to disconnect the main pump variable cylinder from the two-position six-way hydraulic control valve 2032, so as to prevent the second working oil port of the third reversing valve 502 from outputting hydraulic oil to the main pump variable cylinder through the two-position six-way hydraulic control valve 2032 and affecting the normal operation of the main pump 1.

[0082] Finally, if Figure 8 As shown, this embodiment further includes an auxiliary valve group 9. The auxiliary valve group 9 includes an accumulator 901, a fourth reversing valve 902, and two brake oil circuits. The two brake oil circuits are respectively connected to the gear drive brake cylinder 204 and the wheel drive brake cylinder 302. The oil inlet of the fourth reversing valve 902 is connected to the accumulator 901, and the working oil port of the fourth reversing valve 902 is respectively connected to the two brake oil circuits, so as to control the gear and wheel brake of the rack vehicle through the hydraulic system.

[0083] Among them, the fourth reversing valve 902 is a two-position three-way electromagnetic ball valve. When the fourth reversing valve 902 is energized, the fourth reversing valve 902 conducts the oil inlet and the working oil port, so that the accumulator 901 outputs oil pressure to the gear drive brake cylinder 204 and the wheel drive brake cylinder 302, thereby releasing the gear and wheel brakes. When the fourth reversing valve 902 is not energized, the fourth reversing valve 902 conducts the oil return port and the working oil port, and the hydraulic oil in the gear drive brake cylinder 204 and the wheel drive brake cylinder 302 can flow back to the oil tank, thereby braking the gear and wheel. In specific implementation, the second auxiliary pump 903 is arranged in the auxiliary valve group 9, and the auxiliary oil circuit is connected to the accumulator 901, that is, the accumulator 901 is connected to the G oil port of the variable valve group 203, so that the accumulator 901 can provide oil pressure to the oil inlet of the variable control valve 2031.

[0084] In summary, the power switching hydraulic system of the rack vehicle of this embodiment, by setting the wheel drive motor, enables the rack vehicle to drive the wheels through the wheel drive motor under the condition of no slope, realizes the wheel adhesion drive of the rack vehicle, so as to meet the requirements of fast and efficient driving of the rack vehicle on a straight track. At the same time, the setting of the switching valve group 4 and the functional valve group 5 can realize the switching of the rack vehicle between the gear drive mode and the wheel adhesion drive mode, so that the rack vehicle can drive on complex terrain and steep slopes through gear drive, and can also meet the characteristics of fast and efficient driving of the rack vehicle on a straight track through wheel adhesion drive. And through the setting of the master control valve 6, the switching valve group 4 and the functional valve group 5 can be controlled to switch the state synchronously, so as to improve the speed of the drive mode switching and ensure the stability during the drive mode switching process.

[0085] Embodiment 2

[0086] The present embodiment relates to a rack rail vehicle, in which the rack rail vehicle power switching hydraulic system in the first embodiment is provided.

[0087] In this embodiment, through the setting of the above-mentioned rack vehicle power switching hydraulic system, the switching valve group 4 and the functional valve group 5 can drive the gear drive motor 2 or the wheel drive motor 3 to run and drive the rack vehicle to travel, and when one motor is running, the other motor that is not running is placed in a free wheel working state that can rotate freely, so that during the running of the rack vehicle, the rack vehicle can switch between the gear drive mode and the wheel adhesion drive mode, so that the rack vehicle can not only travel on complex terrain and steep slopes through gear drive, but also meet the characteristics of fast and efficient running of the rack vehicle on a straight track through wheel adhesion drive, so as to ensure the smooth running of the rack vehicle under different driving conditions. At the same time, through the setting of the master control valve 6, the switching valve group 4 and the functional valve group 5 can be controlled to switch the state synchronously, so as to increase the speed of power switching and ensure the stability during the power switching process.

[0088] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A power switching hydraulic system for a rack rail vehicle, characterized in that: It comprises a main pump (1), a gear drive motor (2), a wheel drive motor (3), a switching valve group (4), and a functional valve group (5); The gear drive motor (2) is transmission-connected to the gear, and the wheel drive motor (3) is transmission-connected to the wheel; The switching valve group (4) is connected between the main pump (1), the gear drive motor (2), and the wheel drive motor (3); The switching valve group (4) has a gear drive state in which the gear drive motor (2) and the main pump (1) are connected in series, and a wheel drive state in which the wheel drive motor (3) and the main pump (1) are connected in series; A first freewheel valve group (201) is connected between the two oil ports of the gear drive motor (2), and a second freewheel valve group (301) is connected between the two oil ports of the wheel drive motor (3); The functional valve group (5) has a first state for controlling the second freewheel valve group (301) to conduct the two oil ports of the wheel drive motor (3), and a second state for controlling the first freewheel valve group (201) to conduct the two oil ports of the gear drive motor (2).

2. The rack rail vehicle power switching hydraulic system according to claim 1, characterized in that: It also includes a master control valve (6) and a first auxiliary pump (7); The oil inlet of the master control valve (6) is connected to the first auxiliary pump (7), and the oil return port of the master control valve (6) is connected to the oil tank; The first auxiliary pump (7) is capable of providing control oil pressure to the switching valve group (4) and the functional valve group (5) through the working oil port of the master control valve (6), so as to drive the switching valve group (4) to switch between the gear drive state and the wheel drive state, and drive the functional valve group (5) to switch between the first state and the second state.

3. The rack rail vehicle power switching hydraulic system according to claim 2, characterized in that: The switching valve group (4) comprises a first gear-driven cartridge valve (401), a second gear-driven cartridge valve (402), a first wheel-driven cartridge valve (403), a second wheel-driven cartridge valve (404) and a first reversing valve (405); An oil port of the main pump (1) is in communication with the first oil ports of the first gear drive cartridge valve (401) and the first wheel drive cartridge valve (403), and another oil port of the main pump (1) is in communication with the first oil ports of the second gear drive cartridge valve (402) and the second wheel drive cartridge valve (404); The second oil ports of the first gear drive cartridge valve (401) and the second gear drive cartridge valve (402) are respectively connected to the two oil ports of the gear drive motor (2), and the second oil ports of the first wheel drive cartridge valve (403) and the second wheel drive cartridge valve (404) are respectively connected to the two oil ports of the wheel drive motor (3); The oil inlet of the first reversing valve (405) is connected to one of the two oil ports of the main pump (1), and the oil return port of the first reversing valve (405) is connected to the oil tank; The first working oil port of the first reversing valve (405) is connected to the control oil ports of the first gear drive cartridge valve (401) and the second gear drive cartridge valve (402), and the second working oil port of the first reversing valve (405) is connected to the control oil ports of the first wheel drive cartridge valve (403) and the second wheel drive cartridge valve (404); The control oil port of the first reversing valve (405) is connected to the working oil port of the master control valve (6).

4. The rack rail vehicle power switching hydraulic system according to claim 2, characterized in that: The functional valve group (5) comprises a second reversing valve (501); The oil inlet of the second reversing valve (501) is connected to the first auxiliary pump (7), and the oil return port of the second reversing valve (501) is connected to the oil tank; The first working oil port of the second reversing valve (501) is capable of inputting oil pressure to the second free-wheel valve group (301); The second working oil port of the second reversing valve (501) is capable of inputting oil pressure to the first free wheel valve group (201); The control oil port of the second reversing valve (501) is connected to the working oil port of the master control valve (6).

5. The rack rail vehicle power switching hydraulic system according to claim 4, characterized in that: The first free-wheel valve assembly (201) comprises a first stop valve (2011), and the second free-wheel valve assembly (301) comprises a second stop valve (3011); The control oil port of the first stop valve (2011) is connected to the second working oil port of the second reversing valve (501), and the control oil port of the second stop valve (3011) is connected to the first working oil port of the second reversing valve (501); When the second reversing valve (501) provides oil pressure to the control oil ports of the first stop valve (2011) and the second stop valve (3011), the first stop valve (2011) can conduct the two oil ports of the gear drive motor (2), and the second stop valve (3011) can conduct the two oil ports of the wheel drive motor (3).

6. The rack rail vehicle power switching hydraulic system according to claim 5, characterized in that: The second stop valve (3011) is configured as two connected in series, and an oil return oil path connected to the oil tank is provided between the two second stop valves (3011); And / or, the two oil ports of the gear-driven motor (2) are connected to the second auxiliary pump (903) via an oil replenishment circuit.

7. The rack rail vehicle power switching hydraulic system according to claim 2, characterized in that: The functional valve group (5) further includes a third reversing valve (502); The oil inlet of the third reversing valve (502) is connected to the first auxiliary pump (7), and the oil return port of the third reversing valve (502) is connected to the oil tank; The first working port of the third reversing valve (502) is connected to the housing oil discharge port of the wheel drive motor (3) through two branches, one of the branches is connected in series with a pressure reducing valve (503), and the other branch is provided with a one-way valve (504); The control oil port of the third reversing valve (502) is in communication with the working oil port of the master control valve (6).

8. The rack rail vehicle power switching hydraulic system according to claim 7, characterized in that: The gear-driven motor (2) is a variable displacement motor, and the two chambers of the single-piston variable displacement cylinder (202) of the gear-driven motor (2) are respectively connected to the variable displacement valve group (203) through a first variable displacement oil circuit and a second variable displacement oil circuit; The variable valve group (203) comprises a variable control valve (2031), an oil inlet of the variable control valve (2031) is connected to an auxiliary oil circuit, an oil return port of the variable control valve (2031) is connected to the oil tank, and a working oil port of the variable control valve (2031) is connected to the second variable oil circuit; The first variable oil circuit can be connected to any oil port of the gear-driven motor (2), and connected to the auxiliary oil circuit; The first control oil port of the variable control valve (2031) is connected to the second working oil port of the third reversing valve (502), and the second control oil port of the variable control valve (2031) is connected to the first variable oil circuit.

9. The rack rail vehicle power switching hydraulic system according to any one of claims 1 to 8, characterized in that: Also includes an auxiliary valve group (9); The auxiliary valve group (9) comprises an accumulator (901), a fourth reversing valve (902) and two brake oil circuits; The two brake oil circuits are respectively connected to the gear-driven brake cylinder (204) and the wheel-driven brake cylinder (302); The oil inlet of the fourth reversing valve (902) is connected to the accumulator (901), and the two working oil ports of the fourth reversing valve (902) are respectively connected to the two brake oil circuits.

10. A rack rail vehicle, characterized in that: The rack rail vehicle is provided with the rack rail vehicle power switching hydraulic system according to any one of claims 1 to 9.

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