Hydraulic motor integrated control valve group of first rope replacing vehicle

Abstract

The invention relates to a hydraulic motor integrated control valve group of a first rope changing vehicle, which is characterized in that a port A of an electromagnetic relief valve and a port P1 of a third one-way valve are connected in parallel to a main pump oil inlet P1 of a valve block, and the third one-way valve and a fourth one-way valve are connected in series between the main pump oil inlet P1 and an auxiliary pump oil inlet P2 of the valve group; the electro-hydraulic directional control valve and the first one-way valve are connected between the communication position of the third one-way valve and the fourth one-way valve and a main oil return port T of the valve set in series, the overflow valve with the remote pressure regulating connector is connected between the electro-hydraulic directional control valve and the main oil return port T, and the second one-way valve is connected between an oil supplementing port P3 of the valve set and a hydraulic motor connecting oil port B. A main pump pressure gauge connector S1 is connected with a main pump oil inlet P1, and a working pressure measuring opening S2 is connected with a hydraulic motor connecting oil opening A of the valve set. The overflow valve, the oil supplementing one-way valve, the main pump one-way valve and the like which are distributed in a scattered mode are concentrated on the valve blocks where the electromagnetic overflow valve and the electro-hydraulic reversing valve are located, so that peripheral pipelines are greatly simplified, and meanwhile the number of connectors and the leakage risk are reduced.

Description

Technical Field

[0001] The invention belongs to the technical field of special engineering machinery for mines, and in particular relates to a hydraulic motor integrated control valve group of a first rope changing vehicle. Background Art

[0002] The first rope changing vehicle is the main type of engineering machinery for mechanized first rope changing in friction hoisting of mine shafts. Its hydraulic motor is the main working mechanism of the first rope changing vehicle, which involves safety and is of vital importance. At this stage, the rope changing vehicle is in a period of rapid development, and its stability and reliability are still slightly insufficient. In particular, the rope changing vehicle is a kind of construction machinery that has to be operated between various construction sites across the country. Under the long-term bumpy road, it is very easy to have problems or failures such as loose pipes, bracket deformation, pipe vibration, and leakage. In addition, the mobile machinery itself has a small space and is not easy to repair, which brings considerable trouble to the construction of the project. Therefore, it is necessary to adopt integrated valve group technology to effectively reduce the complexity of the hydraulic pipeline, increase the maintenance space, reduce the number of pipeline joints, optimize the oil circuit, make the flow smoother, and reduce the resistance, thereby further improving the performance of the equipment. Summary of the invention

[0003] In order to overcome the shortcomings of the above-mentioned prior art, the present invention provides a hydraulic motor integrated control valve group for the first rope changing vehicle, which has the advantages of high integration, stable and reliable operation, and small flow resistance, and solves the problem of low integration and small maintenance space of the hydraulic motor control circuit valve group of the first rope changing vehicle.

[0004] The present invention is realized through the following technical scheme: a hydraulic motor integrated control valve group of a first rope changing vehicle, including an electromagnetic overflow valve, an overflow valve with a remote pressure regulating function, an electro-hydraulic reversing valve, a first non-return valve, a second non-return valve, a third non-return valve, and a fourth non-return valve, characterized in that it also includes a hydraulic motor connecting oil port A port, a hydraulic motor connecting oil port B port, a main oil return port T port, an oil return confluence port CT port of an auxiliary pump and a remote pressure regulating valve, etc., a main pump oil inlet port P1 port, an auxiliary pump oil inlet port P2 port, an oil replenishment port P3 port, a main pump pressure gauge interface S1 port, a working pressure gauge interface S2 port and a remote pressure regulating valve interface X port; The A port of the electromagnetic overflow valve and the P1 port of the third one-way valve are connected in parallel to the main pump oil inlet P1 port of the valve block, the B port of the electromagnetic overflow valve is connected to the main oil return port T port of the valve block, the P2 port of the third one-way valve and the P2 port of the fourth one-way valve are connected in parallel to the P port of the electro-hydraulic reversing valve, the P1 port of the fourth one-way valve is connected to the auxiliary pump oil inlet P2 port of the valve block, the P port and the T port of the electro-hydraulic reversing valve are connected in series with the P1 port and the P2 port of the first one-way valve to the third one-way valve and Between the connection point of the fourth one-way valve and the main oil return port T of the valve group, the A port and B port of the relief valve with a remote pressure regulating interface are respectively connected to the A port of the electro-hydraulic reversing valve and the main oil return port T of the valve block, the P1 port and P2 port of the second one-way valve are respectively connected to the oil replenishment port P3 port of the valve block and the hydraulic motor connecting oil port B port, the main pump pressure gauge interface S1 port is connected to the main pump oil inlet port P1 port, and the working pressure measuring port S2 port is connected to the hydraulic motor connecting oil port A port of the valve group.

[0005] A third one-way valve is provided between the main pump oil inlet P1 and the P port of the electro-hydraulic reversing valve, and the third one-way valve is used to prevent the electro-hydraulic reversing valve and the oil entering through the auxiliary pump oil inlet P2 from flowing back to the main pump oil inlet P1.

[0006] A fourth one-way valve is provided between the auxiliary pump oil inlet P2 and the P port of the electro-hydraulic reversing valve, and the fourth one-way valve is used to prevent the electro-hydraulic reversing valve and the oil entering through the main pump oil inlet P1 from flowing back to the auxiliary pump oil inlet P2.

[0007] A first one-way valve is provided between the main oil return port T and the T port of the electro-hydraulic reversing valve, and the first one-way valve is used to prevent all oil directly connected to the main oil return port T from flowing back to the T port side of the electro-hydraulic reversing valve.

[0008] A second one-way valve is arranged between the oil replenishing port P3 and the hydraulic motor connecting oil port B. The second one-way valve is used to prevent the oil in the hydraulic motor connecting oil port B from flowing back to the oil replenishing port P3 on the one hand, and to replenish oil from the oil replenishing port P3 to the hydraulic motor connecting oil port B on the other hand.

[0009] The overflow valve with remote pressure regulating function is connected to the A port of the electro-hydraulic reversing valve, and the second one-way valve is connected to the B port of the electro-hydraulic reversing valve.

[0010] The beneficial effects of the present invention are as follows: the (manual) relief valve, oil replenishment check valve, main pump check valve, auxiliary pump check valve, pipeline pressure measuring port, auxiliary pump independent oil return port, etc., which were originally dispersedly arranged, are concentrated on the valve block where the electromagnetic relief valve and the electro-hydraulic reversing valve are located, so that the peripheral pipelines are greatly simplified, the maintenance space is increased, and the number of joints and the risk of leakage are reduced; the (manual) relief valve is replaced by a remote pressure-regulated relief valve, so that the valve front cavity is smaller, the valve response is faster, and the driver's nearby operation performance is maintained; at the same time, the connecting pipelines between the integrated valves are greatly shortened, the flow path is smoother, the resistance is smaller, which is conducive to improving the efficiency of the system. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] The present invention is further described below with reference to the accompanying drawings and embodiments.

[0012] Figure 1 It is a schematic diagram of the overall structure of the hydraulic motor control valve group of the first rope changing vehicle of the present invention; Figure 2 It is an application schematic diagram of the hydraulic motor control valve group of the first rope changing vehicle of the present invention.

[0013] In the figure: 1. Solenoid overflow valve; 2. First one-way valve; 3. Second one-way valve; 4. Overflow valve with remote pressure regulating interface; 5. Third one-way valve; 6. Electro-hydraulic reversing valve; 7. Fourth one-way valve; 8. Main hydraulic pump; 9. Return oil radiator; 10. Return oil back pressure valve; 11. Hydraulic motor; 12. Remote pressure regulating valve. DETAILED DESCRIPTION

[0014] like Figure 1 As shown, in this embodiment, a hydraulic motor integrated control valve group of a first rope changing vehicle includes a solenoid relief valve, a relief valve with a remote pressure regulating function, an electro-hydraulic reversing valve, a first non-return valve, a second non-return valve, a third non-return valve, and a fourth non-return valve, and also includes a hydraulic motor connecting oil port A, a hydraulic motor connecting oil port B, a main return oil port T, an oil return confluence port CT of an auxiliary pump and a remote pressure regulating valve, etc., a main pump oil inlet port P1, an auxiliary pump oil inlet port P2, an oil replenishment port P3, a main pump pressure gauge interface S1, a working pressure gauge interface S2, and a remote pressure regulating valve interface X; The A port of the electromagnetic overflow valve (1) and the P1 port of the third one-way valve (5) are connected in parallel to the main pump oil inlet port P1 of the valve block, the B port of the electromagnetic overflow valve (1) is connected to the main oil return port T of the valve block, the P2 port of the third one-way valve (5) and the P2 port of the fourth one-way valve (7) are connected in parallel to the P port of the electro-hydraulic reversing valve (6), the P1 port of the fourth one-way valve (7) is connected to the auxiliary pump oil inlet port P2 of the valve block, the P port and the T port of the electro-hydraulic reversing valve (6) are connected in series with the P1 port and the P2 port of the first one-way valve (2). Between the connection point between the third check valve (5) and the fourth check valve (7) and the main oil return port T of the valve group, the A port and the B port of the overflow valve (4) with a remote pressure regulating interface are respectively connected to the A port of the electro-hydraulic reversing valve (6) and the main oil return port T of the valve block, the P1 port and the P2 port of the second check valve (3) are respectively connected to the oil replenishment port P3 port of the valve block and the hydraulic motor connecting oil port B port, the main pump pressure gauge interface S1 port is connected to the main pump oil inlet port P1 port, and the working pressure measuring port S2 port is connected to the hydraulic motor connecting oil port A port of the valve group.

[0015] A third one-way valve is provided between the main pump oil inlet P1 and the P port of the electro-hydraulic reversing valve, and the third one-way valve is used to prevent the electro-hydraulic reversing valve and the oil entering through the auxiliary pump oil inlet P2 from flowing back to the main pump oil inlet P1.

[0016] A fourth one-way valve is provided between the auxiliary pump oil inlet P2 and the P port of the electro-hydraulic reversing valve, and the fourth one-way valve is used to prevent the electro-hydraulic reversing valve and the oil entering through the main pump oil inlet P1 from flowing back to the auxiliary pump oil inlet P2.

[0017] A first one-way valve is provided between the main oil return port T and the T port of the electro-hydraulic reversing valve, and the first one-way valve is used to prevent all oil directly connected to the main oil return port T from flowing back to the T port side of the electro-hydraulic reversing valve.

[0018] A second one-way valve is arranged between the oil replenishing port P3 and the hydraulic motor connecting oil port B. The second one-way valve is used to prevent the oil in the hydraulic motor connecting oil port B from flowing back to the oil replenishing port P3 on the one hand, and to replenish oil from the oil replenishing port P3 to the hydraulic motor connecting oil port B on the other hand.

[0019] The overflow valve with remote pressure regulating function is connected to the A port of the electro-hydraulic reversing valve, and the second one-way valve is connected to the B port of the electro-hydraulic reversing valve.

[0020] like Figure 2As shown, the specific application of the present invention includes a main hydraulic pump 8 connected to the main pump oil inlet P1, an oil return radiator 9 and an oil return back pressure valve 10 connected in series between the main oil return port T and the oil tank, an oil replenishment port P3 connected between the oil return radiator 9 and the oil return back pressure valve 10, a hydraulic motor 11 connected to the hydraulic motor connecting oil port A and the hydraulic motor connecting oil port B, a remote pressure regulating valve 12 connected between the remote pressure regulating valve interface X and the oil return confluence port CT of the auxiliary pump and the remote pressure regulating valve, etc., the oil return port of the auxiliary pump is also connected to the oil return confluence port CT of the auxiliary pump and the remote pressure regulating valve, etc., the oil inlet of the auxiliary pump is connected to the auxiliary pump oil inlet P2, the main pump pressure gauge is connected to the main pump pressure gauge interface S1, and the working pressure gauge is connected to the working pressure gauge interface S2.

[0021] When the large pump supplies oil and the coil of the electromagnetic relief valve 8 is not energized, the oil pumped out by the large pump enters through the main pump oil inlet P1, passes through the electromagnetic relief valve 1, flows out from the main oil return port T, and then flows back to the oil tank through the return oil radiator 9 and the back pressure check valve 10. This is the unloading condition.

[0022] When the large pump supplies oil and the upper coil of the electromagnetic overflow valve 1 and the electro-hydraulic reversing valve 6 is energized, the oil pumped out by the large pump enters through the main pump oil inlet port P1, passes through the third check valve (5), the P port and the B port of the electro-hydraulic reversing valve 6, and then flows out from the hydraulic motor connecting oil port B of the valve block, passes through the hydraulic motor 11, and flows into the hydraulic motor connecting oil port A of the valve block, and then passes through the A port and the T port of the electro-hydraulic reversing valve 6 and the first check valve (2), and then flows out from the main return oil port T, and finally flows back to the oil tank through the radiator 9 and the back pressure check valve 10. This is the fast rope feeding condition.

[0023] When the large pump does not supply oil, the coil of the electromagnetic overflow valve 1 is not energized, and the auxiliary pump oil inlet P2 is supplied by the auxiliary pump and the upper coil of the electro-hydraulic reversing valve 6 is energized, the oil pumped out by the auxiliary pump enters through the auxiliary pump oil inlet P2, passes through the fourth non-return valve (7), the P port and the B port of the electro-hydraulic reversing valve 6, flows out from the hydraulic motor connecting oil port B port, flows into the hydraulic motor connecting oil port A port through the hydraulic motor 11, and then flows out from the main return oil port T port through the A port and the T port of the electro-hydraulic reversing valve 6 and the first non-return valve (2), and finally flows back to the oil tank through the radiator 9 and the back pressure non-return valve 10. This is the slow rope feeding condition.

[0024] When the large pump supplies oil and the lower coil of the electromagnetic overflow valve 1 and the electro-hydraulic reversing valve 6 is energized, the oil pumped out by the large pump enters through the main pump oil inlet port P1, passes through the third check valve (5), the P port and the A port of the electro-hydraulic reversing valve 6, and then flows out from the hydraulic motor connecting oil port A port, passes through the hydraulic motor 11, and flows into the hydraulic motor connecting oil port B port of the valve block, and then passes through the B port and the T port of the electro-hydraulic reversing valve 6 and the first check valve (2), and then flows out from the main return oil port T port, and finally flows back to the oil tank through the radiator 9 and the back pressure check valve 10. This is the fast rope retraction condition.

[0025] When the large pump does not supply oil, the coil of the electromagnetic overflow valve 1 is not energized, and the auxiliary pump oil inlet P2 is supplied by the auxiliary pump and the lower coil of the electro-hydraulic reversing valve 6 is energized, the oil pumped out by the auxiliary pump enters through the auxiliary pump oil inlet P2, passes through the fourth non-return valve (7), the P port and the A port of the electro-hydraulic reversing valve 6, and then flows out from the hydraulic motor connecting oil port A port, passes through the hydraulic motor 11, and flows into the hydraulic motor connecting oil port B port of the valve block, and then passes through the B port and the T port of the electro-hydraulic reversing valve 6 and the first non-return valve (2), and then flows out from the main return oil port T port, and finally flows back to the oil tank through the radiator 9 and the back pressure non-return valve 10. This is the slow rope retracting condition.

[0026] In the slow rope-collecting state, when the load resistance of the hydraulic motor 11 gradually increases and equals the driving force of the auxiliary pump, it is also called the pre-tensioning condition. When the load resistance continues to increase and starts to work (the load resistance causes the hydraulic motor 11 to start reverse rotation), the system will switch to the follow-up rope-releasing condition. At this time, the hydraulic motor 11 is in the working state of pumping oil. The pressure oil pumped out by it flows into the hydraulic motor connecting oil port A of the valve block. The inflowing oil flows out through the A port and the P port of the electro-hydraulic reversing valve 6 to the P2 port of the third check valve 5 and the fourth check valve 7, which is blocked, and the auxiliary pump oil inlet port P2 of the valve block cannot be supplied with oil. The other way flows out through the A port and the B port of the overflow valve (4) with a remote pressure regulating function and then flows out from the main return oil port T port, which increases the pressure of the P2 port of the first check valve 2. The oil flowing out from the main return oil port T port flows through the radiator 9 and then flows back into the valve block from the oil replenishing port P3 port. The inflowing oil flows out through the B port and the T port of the electro-hydraulic reversing valve 6 and then is blocked at the P1 port of the first check valve 2. The other way flows out from the hydraulic motor connecting oil port B through the second check valve (3) and returns to the hydraulic motor 11.

[0027] This system requires that the opening pressure of the external back pressure check valve 10 is greater than the opening pressure of the second check valve (3) on the valve block.

Claims

1. A hydraulic motor integrated control valve group for a first rope changing vehicle, comprising an electromagnetic relief valve (1), a relief valve with a remote pressure regulating function (4), an electro-hydraulic reversing valve (6), a first non-return valve (2), a second non-return valve (3), a third non-return valve (5), and a fourth non-return valve (7), characterized in that: It also includes the hydraulic motor oil connection port A, the hydraulic motor oil connection port B, the main oil return port T, the return oil confluence port CT of the auxiliary pump and the remote pressure regulating valve, the main pump oil inlet port P1, the auxiliary pump oil inlet port P2, the oil replenishment port P3, the main pump pressure gauge interface S1, the working pressure gauge interface S2 and the remote pressure regulating valve interface X; The A port of the electromagnetic overflow valve (1) and the P1 port of the third one-way valve (5) are connected in parallel to the main pump oil inlet port P1 of the valve block, the B port of the electromagnetic overflow valve (1) is connected to the main oil return port T of the valve block, the P2 port of the third one-way valve (5) and the P2 port of the fourth one-way valve (7) are connected in parallel to the P port of the electro-hydraulic reversing valve (6), the P1 port of the fourth one-way valve (7) is connected to the auxiliary pump oil inlet port P2 of the valve block, the P port and the T port of the electro-hydraulic reversing valve (6) are connected in series with the P1 port and the P2 port of the first one-way valve (2). Between the connection point between the third check valve (5) and the fourth check valve (7) and the main oil return port T of the valve group, the A port and the B port of the overflow valve (4) with a remote pressure regulating interface are respectively connected to the A port of the electro-hydraulic reversing valve (6) and the main oil return port T of the valve block, the P1 port and the P2 port of the second check valve (3) are respectively connected to the oil replenishment port P3 port of the valve block and the hydraulic motor connecting oil port B port, the main pump pressure gauge interface S1 port is connected to the main pump oil inlet port P1 port, and the working pressure measuring port S2 port is connected to the hydraulic motor connecting oil port A port of the valve group.

2. The hydraulic motor integrated control valve group of the first rope changing vehicle according to claim 1 is characterized in that: A third one-way valve (5) is provided between the main pump oil inlet port P1 and the port P of the electro-hydraulic reversing valve (6), and the third one-way valve (5) is used to prevent the electro-hydraulic reversing valve (6) and the oil entering through the auxiliary pump oil inlet port P2 from flowing back toward the main pump oil inlet port P1.

3. The hydraulic motor integrated control valve group of the first rope changing vehicle according to claim 1 is characterized in that: A fourth one-way valve (7) is provided between the auxiliary pump oil inlet port P2 and the port P of the electro-hydraulic reversing valve (6), and the fourth one-way valve (7) is used to prevent the electro-hydraulic reversing valve (6) and the oil entering through the main pump oil inlet port P1 from flowing back toward the auxiliary pump oil inlet port P2.

4. The hydraulic motor integrated control valve group of the first rope changing vehicle according to claim 1 is characterized in that: A first one-way valve (2) is provided between the main oil return port T and the T port of the electro-hydraulic reversing valve (6), and the first one-way valve (2) is used to prevent all oil directly connected to the main oil return port T from flowing back to the T port side of the electro-hydraulic reversing valve (6).

5. The hydraulic motor integrated control valve group of the first rope changing vehicle according to claim 1 is characterized in that: A second one-way valve (3) is provided between the oil replenishing port P3 and the hydraulic motor connecting oil port B. The second one-way valve (3) is used, on the one hand, to prevent the oil in the hydraulic motor connecting oil port B from flowing back toward the oil replenishing port P3, and, on the other hand, to replenish oil from the oil replenishing port P3 to the hydraulic motor connecting oil port B.

6. The hydraulic motor integrated control valve group of the first rope changing vehicle according to claim 1 is characterized in that: The overflow valve (4) with remote pressure regulating function is connected to the A port of the electro-hydraulic reversing valve (6), and the second one-way valve (3) is connected to the B port of the electro-hydraulic reversing valve (6).

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