Hydraulic control system for stepping type self-moving tail

Abstract

The utility model relates to the technical field of stepping type self-moving machine tails, in particular to a stepping type self-moving machine tail hydraulic control system which comprises an oil return tank, a hydraulic pump, a first reversing valve, a plurality of telescopic hydraulic cylinders, an on-off valve and a second reversing valve. An oil return port of the first reversing valve is communicated with the oil return tank, an oil port of the telescopic hydraulic cylinder is correspondingly connected with a working oil port of the first reversing valve, an oil way between the first reversing valve and the telescopic hydraulic cylinder is connected and disconnected through the on-off valve, an oil inlet of the second reversing valve is communicated with an outlet of the hydraulic pump, and an oil return port of the second reversing valve is communicated with the oil return tank. When the first reversing valve is in the working state, the on-off valve and the second reversing valve are both in the off state, and when the first reversing valve is in the working state, the on-off valve is in the working state, and the second reversing valve is in the off state. According to the utility model, synchronous lifting control can be carried out on a plurality of telescopic oil cylinders, and independent lifting control can also be carried out on the telescopic oil cylinders.

Description

Technical Field

[0001] The utility model relates to the technical field of walking type self - moving machine tails, and more specifically, to a hydraulic control system for a walking type self - moving machine tail. Background Technique

[0002] A walking type self - moving machine tail is a moving device used at the tail of a belt conveyor, which allows the conveyor to move forward automatically during tunneling operations, thereby improving work efficiency and reducing manual operations.

[0003] A walking type self - moving machine tail usually includes key components such as a frame, guide rails, a lifting mechanism, and a driving mechanism. Among them, the lifting mechanism includes multiple telescopic cylinders, and during use, the lifting of the telescopic cylinders is synchronously controlled by a multi - way valve group.

[0004] However, this method cannot achieve independent lifting control of some of the telescopic cylinders in certain scenarios. For example, when the support plane in the working area is uneven, and at this time, the height of a single bridge needs to be adjusted. In addition, if the multi - way valve group fails, synchronous lifting control cannot be performed, nor can independent lifting control of the telescopic cylinders be carried out. Summary of the Utility Model

[0005] The utility model aims to solve at least one of the technical problems existing in the prior art. For this reason, the utility model provides a hydraulic control system for a walking type self - moving machine tail, aiming to be able to simultaneously perform synchronous lifting control on multiple telescopic cylinders and also perform independent lifting control on the telescopic cylinders among them.

[0006] A hydraulic control system for a walking type self - moving machine tail according to an embodiment of the utility model includes: an oil return tank, a hydraulic pump, a first reversing valve, multiple telescopic hydraulic cylinders, a on - off valve, and a second reversing valve. The inlet of the hydraulic pump is connected to the oil return tank. The first reversing valve is used to change the flow direction of its working oil ports. The inlet port of the first reversing valve is communicated with the outlet of the hydraulic pump, and the oil return port of the first reversing valve is communicated with the oil return tank. Both oil ports of each telescopic hydraulic cylinder are correspondingly connected to the two working oil ports of the first reversing valve. The on - off valve is used to open and close the oil circuit between the first reversing valve and the telescopic hydraulic cylinder. The second reversing valve is used to change the flow direction of its working oil ports. The inlet port of the second reversing valve is communicated with the outlet of the hydraulic pump, the oil return port of the second reversing valve is communicated with the oil return tank, and the working oil ports of the second reversing valve are correspondingly connected to the two oil ports of the telescopic hydraulic cylinder. When the second reversing valve is in the working state, the first reversing valve and the on - off valve are both in the off state. When the first reversing valve is in the working state, the on - off valve is in the working state, and the second reversing valve is in the off state.

[0007] The beneficial effects of the present utility model at least include: By providing a cut-off valve in the circuit of the oil return tank, hydraulic pump, first reversing valve, and telescopic hydraulic cylinder, synchronous lifting control of multiple telescopic cylinders can be carried out, or the synchronous lifting control can be stopped. At this time, the circuit of the oil return tank, hydraulic pump, second reversing valve, and telescopic hydraulic cylinder can perform independent lifting control on a single telescopic cylinder. When it is necessary to resume synchronous lifting control, only make the second reversing valve in the off state and open the cut-off valve; In addition, by providing a cut-off valve, it can prevent the inability to perform independent lifting control on a single telescopic cylinder and stop the synchronous lifting control of multiple telescopic cylinders when the first reversing valve fails.

[0008] In addition, according to the above-mentioned walking type self-shifting shearer tail hydraulic control system of the present utility model, it may further have the following additional technical features:

[0009] Further, the first reversing valve is a three-position four-way electromagnetic reversing valve with a manual function.

[0010] Further, the cut-off valve is a two-position four-way electromagnetic reversing valve, and the corresponding oil ports are in two-way conduction when it is conducting.

[0011] Further, the cut-off valve is a two-position four-way electromagnetic reversing valve with a manual function.

[0012] Further, the second reversing valve is a three-position four-way electromagnetic reversing valve.

[0013] Further, the second reversing valve is a three-position four-way electromagnetic reversing valve with a manual function.

[0014] Further, a flow dividing and collecting valve is provided between adjacent telescopic hydraulic cylinders. One connection port of the flow dividing and collecting valve is connected to one of the oil ports of the first reversing valve, and the remaining two connection ports of the flow dividing and collecting valve are respectively connected to the chambers of the corresponding telescopic hydraulic cylinders that are not connected to the oil return tank.

[0015] Further, a speed control valve is connected in series on the working oil path of the second reversing valve.

[0016] Further, the hydraulic pump includes a variable pump and a variable control valve group. The variable control valve group is used to sense the load feedback pressure and adjust the outlet flow of the variable pump according to the pressure difference between the outlet pressure of the variable pump and the load feedback pressure.

[0017] Furthermore, the variable control valve group includes a pressure cut-off valve and a load-sensing valve. The working oil port A2 and the control oil port K3 of the pressure cut-off valve, as well as the working oil port B2 and the control oil port K1 of the load-sensing valve, are all connected to the outlet of the variable pump. The working oil port A1 of the pressure cut-off valve is connected to the rodless cavity of the variable pump and is connected back to the oil tank through hydraulic resistances R2 and R3. The working oil port A3 of the pressure cut-off valve is connected to the working oil port B1 of the load-sensing valve and is connected back to the oil tank through hydraulic resistance R3. The working oil port B3 of the load-sensing valve is connected back to the oil tank through hydraulic resistance R4. The control oil port K2 of the load-sensing valve is connected back to the oil tank through hydraulic resistance R1. The control oil port K4 of the pressure cut-off valve is connected to the oil tank. Description of the Drawings

[0018] Figure 1 is the hydraulic control schematic diagram of the present utility model;

[0019] Figure 2 is the partial enlarged view at S of the embodiment of the present utility model.

[0020] Description of the Main Component Symbols:

[0021] Oil tank 100, filter 110, hydraulic pump 200, variable pump 210, variable control valve group 220, pressure cut-off valve 221, load-sensing valve 222, first reversing valve 300, multiple telescopic hydraulic cylinders 400, on-off valve 500, second reversing valve 600, relief valve 700, flow dividing and collecting valve 800, speed control valve 900.

[0022] The following specific embodiments will further illustrate the present utility model in conjunction with the above-mentioned drawings. Specific Embodiments

[0023] The embodiments of the present utility model will be described in detail below. The examples of the embodiments are shown in the drawings, where the same or similar reference numerals represent the same or similar elements or elements with the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and are only used to explain the present utility model and should not be construed as a limitation to the present utility model.

[0024] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by terms such as up and down, etc., is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present utility model 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 thus should not be construed as a limitation to the present utility model.

[0025] In the description of the present utility model, "a plurality of" refers to more than two. If there is a description of "first" and "second", it is only for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features or implicitly indicating the sequence relationship of the indicated technical features.

[0026] In the description of the present utility model, unless otherwise clearly defined, terms such as "arrangement", "installation", and "connection" should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above terms in the present utility model in combination with the specific content of the technical solution.

[0027] Refer to Figure 1 and Figure 2 As shown in

[0028] In some optional embodiments, such as Figure 1 and Figure 2 As shown, in order to prevent the system from being damaged by excessive system pressure, a relief valve 700 is provided between the outlet N of the hydraulic pump 200 and the oil return tank 100. In actual use, the relief valve 700 is set to a corresponding pressure value according to the usage.

[0029] In some optional embodiments, the first reversing valve 300 is a three-position four-way solenoid reversing valve with a manual function. When the coil is not conducting or the manual lever is not acting, the first reversing valve 300 is in the middle position, at which time the first reversing valve 300 is in a disconnected state, and the hydraulic oil cannot flow through the first reversing valve 300. When the coils on both sides are conducting or the manual lever is acting, the first reversing valve 300 is in the left position or the right position, at which time the first reversing valve 300 is in a connected state, and the hydraulic oil can flow through the first reversing valve 300. In this embodiment, by using a three-position four-way solenoid reversing valve with a manual function, when the coil fails, the manual lever can be used for operation, thereby improving the reliability of the system.

[0030] In some optional embodiments, the on-off valve 500 is a two-position four-way electromagnetic reversing valve, and when it is turned on, the corresponding oil ports are bidirectionally connected, that is, the oil ports C1 and C2 are bidirectionally connected, and the oil ports D1 and D2 are bidirectionally connected. In this way, there is no need to use a three-position four-way electromagnetic reversing valve, thereby reducing the cost of use. At the same time, compared with a three-position four-way electromagnetic reversing valve, the structure is simpler and the reliability of the system can be improved to a certain extent.

[0031] In some optional embodiments, further, the on-off valve 500 adopts a two-position four-way electromagnetic reversing valve with a manual function. When the coil is not conductive or the manual lever is not in effect, the on-off valve 500 is in the right position, at which time the on-off valve 500 is in a disconnected state, and the hydraulic oil cannot flow through the on-off valve 500. When the coil is conductive or the manual lever is in effect, the on-off valve 500 is in the left position, at which time the on-off valve 500 is in a connected state, and the hydraulic oil can flow through the on-off valve 500. In this embodiment, by adopting a two-position four-way electromagnetic reversing valve with a manual function, when the coil fails, the manual lever can be used for operation, thereby further improving the reliability of the system.

[0032] In some alternative embodiments, the second reversing valve 600 is a three-position four-way electromagnetic reversing valve. Preferably, the second reversing valve 600 is a three-position four-way electromagnetic reversing valve with a manual function. When the coil is not energized or the manual lever is not actuated, the second reversing valve 600 is in the middle position, and at this time, the second reversing valve 600 is in the off state, and the hydraulic oil cannot flow through the second reversing valve 600. When the coils on both sides are energized or the manual lever is actuated, the second reversing valve 600 is in the left position or the right position, and at this time, the second reversing valve 600 is in the connected state, and the hydraulic oil can flow through the second reversing valve 600. Since the first reversing valve 300 and the on-off valve 500 are both in the off state at this time, the second reversing valve 600 can be controlled so that the telescopic hydraulic cylinder 400 can switch between the extending and retracting modes. In this embodiment, by using a three-position four-way electromagnetic reversing valve with a manual function, when the coil fails, it can be operated by the manual lever, improving the reliability of the system.

[0033] In some alternative embodiments, as Figure 1 shown, a flow dividing and collecting valve 800 is provided between adjacent telescopic hydraulic cylinders 400. The connection port F1 of the flow dividing and collecting valve 800 is connected to the oil port C2 of the on-off valve 500, and the remaining two connection ports (F2, F3) of the flow dividing and collecting valve are respectively connected to the rod chambers of the two telescopic hydraulic cylinders 400 on its left and right sides. The rodless chambers of the telescopic hydraulic cylinders 400 are connected to the oil port D2 of the on-off valve 500. By utilizing the characteristic that the flow dividing and collecting flow rates of the flow dividing and collecting valve 800 are consistent, the moving speeds of the respective telescopic hydraulic cylinders 400 are kept consistent.

[0034] In some alternative embodiments, as Figure 1 shown, a speed control valve 900 is connected in series on the working oil path of the second reversing valve 600. By adjusting the opening degree of the speed control valve 900, the moving speed of the telescopic hydraulic cylinder 400 can be adjusted and controlled.

[0035] In some alternative embodiments, as Figure 1 and Figure 2 shown, the hydraulic pump 100 includes a variable pump 210 and a variable control valve group 220. The variable control valve group 220 is used to sense the load feedback pressure and adjust the outlet flow rate of the variable pump 210 according to the pressure difference between the outlet pressure of the variable pump 210 and the load feedback pressure. With such a setting, the system oil pressure can be dynamically adjusted according to the load size, achieving the purpose of energy saving.

[0036] In some alternative embodiments, as Figure 2As shown, specifically, the variable control valve group 220 includes a pressure cut-off valve 221 and a load-sensing valve 222. The working oil port A2 and the control oil port K3 of the pressure cut-off valve 221, and the working oil port B2 and the control oil port K1 of the load-sensing valve are all connected to the outlet of the variable pump 210. The working oil port A1 of the pressure cut-off valve 221 is connected to the rodless cavity of the variable pump 210 and is connected back to the oil tank 100 through a liquid resistance R2 and a liquid resistance R3. The working oil port A3 of the pressure cut-off valve 221 is connected to the working oil port B1 of the load-sensing valve 222 and is connected back to the oil tank 100 through a liquid resistance R3. The working oil port B3 of the load-sensing valve 222 is connected back to the oil tank 100 through a liquid resistance R4. The control oil port K2 of the load-sensing valve 222 is connected back to the oil tank 100 through a liquid resistance R1. The control oil port K4 of the pressure cut-off valve 221 is connected to the oil tank 100.

[0037] In this embodiment, when the outlet pressure of the variable pump 210 reaches the set pressure of the pressure cut-off valve 221, it is in the left position. The high-pressure oil output from the outlet of the variable pump 210 enters the rodless cavity of the variable pump 210, causing the variable piston to move to the left. At this time, the output flow rate of the variable pump 210 decreases. When the difference between the pressure at the B2 port and the pressure at the B3 port of the load-sensing valve 222 becomes larger, the load-sensing valve 222 is in the left position. The high-pressure oil output from the outlet of the variable pump 210 enters the rodless cavity of the variable pump 210, causing the variable piston to move to the left. At this time, the output flow rate of the variable pump 210 decreases. Among them, the settings of the liquid resistances R1, R2, R3, and R4 together form a liquid resistance during the process of increasing the displacement, which improves the rapidity and stability of the flow control of the variable pump 210.

[0038] The above has described the embodiments of the present invention in detail with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those of ordinary skill in the art in the relevant technical field, various changes can be made without departing from the gist of the present invention.

Claims

1. A hydraulic control system for a walking self-moving tail, characterized in that: The walking type self-moving tail hydraulic control system includes: Return to the fuel tank; A hydraulic pump, wherein the inlet of the hydraulic pump is connected to the oil return tank; A first reversing valve, used to change the flow direction of its working oil port, the oil inlet of the first reversing valve is connected to the outlet of the hydraulic pump, and the oil return port of the first reversing valve is connected to the oil return tank; A plurality of telescopic hydraulic cylinders, wherein two oil ports of each telescopic hydraulic cylinder are correspondingly connected to two working oil ports of the first reversing valve; An on-off valve, used for opening and closing the oil circuit between the first reversing valve and the telescopic hydraulic cylinder; The second reversing valve is used to change the flow direction of its working oil port, the oil inlet of the second reversing valve is connected to the outlet of the hydraulic pump, the oil return port of the second reversing valve is connected to the oil return tank, and the working oil port of the second reversing valve is correspondingly connected to the two oil ports of the telescopic hydraulic cylinder; when the second reversing valve is in a working state, the first reversing valve and the on-off valve are both in a disconnected state, and when the first reversing valve is in a working state, the on-off valve is in a working state, and the second reversing valve is in a disconnected state.

2. The hydraulic control system for the walking self-moving tail of the machine according to claim 1 is characterized in that: The first reversing valve is a three-position four-way solenoid reversing valve with a manual function.

3. The hydraulic control system for the walking self-moving tail of the machine according to claim 1 is characterized in that: The on-off valve is a two-position four-way electromagnetic reversing valve, and when it is turned on, the corresponding oil ports are bidirectionally conductive.

4. The hydraulic control system for the walking self-moving tail of the machine according to claim 3 is characterized in that: The on-off valve is a two-position four-way electromagnetic reversing valve with a manual function.

5. The hydraulic control system for the walking self-moving tail of claim 1 is characterized in that: The second reversing valve is a three-position four-way solenoid reversing valve.

6. The hydraulic control system for the walking self-moving tail of claim 5, characterized in that: The second reversing valve is a three-position four-way solenoid reversing valve with a manual function.

7. The hydraulic control system for the walking self-moving tail of claim 1, characterized in that: A diverter and collector valve is provided between adjacent telescopic hydraulic cylinders, one connection port of the diverter and collector valve is connected to one of the oil ports of the first reversing valve, and the remaining two connection ports of the diverter and collector valve are respectively connected to the corresponding chambers of the telescopic hydraulic cylinder that are not connected to the return oil tank.

8. The hydraulic control system for the walking self-moving tail of the machine according to claim 1, characterized in that: A speed regulating valve is connected in series to the working oil circuit of the second reversing valve.

9. The hydraulic control system for the walking self-moving tail of claim 1, characterized in that: The hydraulic pump comprises a variable pump and a variable control valve group, wherein the variable control valve group is used to sense load feedback pressure and adjust the outlet flow of the variable pump according to the pressure difference between the outlet pressure of the variable pump and the load feedback pressure.

10. The hydraulic control system for the walking self-moving tail of claim 9, characterized in that: The variable control valve group includes a pressure cut-off valve and a load sensitive valve. The working oil port A2 and the control oil port K3 of the pressure cut-off valve, as well as the working oil port B2 and the control oil port K1 of the load sensitive valve are all connected to the outlet of the variable pump. The working oil port A1 of the pressure cut-off valve is connected to the rodless chamber of the variable pump, and is connected to the return oil tank through hydraulic resistors R2 and R3. The working oil port A3 of the pressure cut-off valve is connected to the working oil port B1 of the load sensitive valve, and is connected to the return oil tank through hydraulic resistor R3. The working oil port B3 of the load sensitive valve is connected to the return oil tank through hydraulic resistor R4. The control oil port K2 of the load sensitive valve is connected to the return oil tank through hydraulic resistor R1. The control oil port K4 of the pressure cut-off valve is connected to the return oil tank.

Images