A hydraulic walking device for underground coal mines

Abstract

The present invention relates to the technical field of monorail cranes, and discloses a hydraulic travel device for underground coal mines, which includes an arc-shaped I-shaped crane rail, an outer ring gear rail, an inner ring gear rail, a crane and a travel gear. The crane is slidably suspended on the arc-shaped I-shaped crane rail, and hydraulic motors are symmetrically arranged on both sides of the crane. A transfer case is arranged on the top of the hydraulic motor for power connection, a travel reducer is arranged on the top of the transfer case for power connection, and the travel reducer is connected to the travel gear for power connection. Compared with the prior art, the advantages of the present invention are: the present invention automatically distributes the hydraulic oil flow of the hydraulic motor for differential speed through the residual mechanical energy difference of the hydraulic oil after the hydraulic motor drives the travel gear, and does not require other control valve groups or external control device operation. The hydraulic oil flow is automatically distributed to achieve differential speed. In addition to providing differential speed when turning, the hydraulic differential mechanism can also improve the energy utilization efficiency of the hydraulic oil to a certain extent when driving in a straight line, and increase the power output of the hydraulic motor.

Description

Technical Field

[0001] The invention relates to the technical field of monorail cranes, in particular to a hydraulic traveling device used in underground coal mines. Background Art

[0002] At present, monorail cranes are often used in coal mines as a means of transporting personnel, equipment and coal mines. They are mainly composed of an I-beam hanging rail hoisted in the tunnel and a crane traveling on the hanging rail. The crane uses an explosion-proof diesel engine or an explosion-proof battery to drive the hydraulic pump station on the vehicle. The hydraulic pump station provides hydraulic oil to the hydraulic motors of each section of the crane's traveling device. The traveling device can be divided into roller type and rack type. The roller type drives the rollers that fit the side walls of the I-beam hanging rail through a hydraulic motor to achieve walking, and the rack type can be divided into single rack and double rack. Both require the installation of racks on the I-beam hanging rail, and the hydraulic motor drives the gears meshing with the racks to achieve walking. The rack type has high power transmission efficiency due to its gear meshing form, and is often used in tunnels with slopes.

[0003] However, with the deepening of coal mining, some coal mines will have tunnels that require climbing and turning at the same time. In this case, the single rack gear cannot fully engage with the curved rack, resulting in reduced power efficiency, poor climbing performance, and easy damage to the rack and gear. The double rack has a difference in the number of internal and external teeth at the turning point, which requires the running gear to have a speed difference. Conventional double rack cranes do not have the ability of hydraulic motor differential output, making it difficult for the crane to turn. Summary of the invention

[0004] The technical problem to be solved by the present invention is that the existing rack-type monorail crane is difficult to travel on a curved track, and a hydraulic traveling device for underground coal mines is provided.

[0005] In order to solve the above technical problems, the technical solution provided by the present invention is: a hydraulic traveling device for underground coal mines, which includes an arc-shaped I-shaped hanging rail, an outer ring gear rail, an inner ring gear rail, a crane and a traveling gear. The crane is slidingly suspended on the arc-shaped I-shaped hanging rail, and hydraulic motors are symmetrically arranged on both sides of the crane. A transfer case is arranged on the top of the hydraulic motor for power connection, a traveling reducer is arranged on the top of the transfer case for power connection, and the traveling gear is connected to the top of the traveling reducer for power connection. The outer ring gear rail is fixedly arranged on the outer ring of the top of the arc-shaped I-shaped hanging rail, and the inner ring gear rail is fixedly arranged on the inner ring of the top. The traveling gears on both sides of the crane are respectively meshed with the outer ring gear rail and the inner ring gear rail.

[0006] The hydraulic motor is composed of an inlet housing, a main housing and an outlet housing which are sleeved and fixed in sequence from top to bottom. A first rotor impeller is rotatably connected in the main housing, and the first rotor impeller is provided with a hollow first output shaft. A second rotor impeller is rotatably connected in the outlet housing, and the second rotor impeller is provided with a second output shaft. The second output shaft passes through the first output shaft and extends above the first output shaft. Both the first output shaft and the second output shaft extend upward into the transfer case, and the first output shaft drives the travel gear through the transfer case.

[0007] A buffer tank is provided at the front end of the crane, and a hydraulic oil inlet pipe is arranged at the bottom of the buffer tank to communicate with the external monorail crane hydraulic pump station. Gear pumps are symmetrically arranged on both sides of the buffer tank, a gear pump inlet is arranged on one side of the gear pump and a gear pump outlet is arranged on the other end. A connecting pipe is provided at the gear pump outlet to communicate with the top of the inlet shell, and the gear pump inlet is connected to the buffer tank, and the second output shaft drives the gear pump through the transfer case.

[0008] Furthermore, a first stator impeller is fixedly arranged in the hydraulic motor, the first rotor impeller is located below the first stator impeller, a second stator impeller is arranged below the first rotor impeller, and the second rotor impeller is located below the second stator impeller.

[0009] Furthermore, an annular liquid inlet is provided on the top of the inlet shell and is connected to the connecting pipe. An expansion flow channel matching the first stator impeller is provided in the inlet shell. The top of the expansion flow channel is connected to the annular liquid inlet, and the bottom extends to the blades of the first stator impeller. A working flow channel matching the first rotor impeller and the second stator impeller is provided in the main shell. The top of the working flow channel is connected to the bottom of the expansion flow channel. A convergent flow channel matching the second rotor impeller is provided in the outlet shell. The top of the convergent flow channel is connected to the working flow channel. A hydraulic oil outlet pipe is provided at the bottom of the outlet shell and is connected to the convergent flow channel.

[0010] Furthermore, the top of the expansion channel extends to the inner circle of the annular liquid inlet, and an overflow ring extending upward is provided between the expansion channel and the annular liquid inlet.

[0011] Furthermore, a first bevel gear is provided at the bottom of the transfer case and is dynamically connected to the first output shaft, a second bevel gear is rotatably connected to the inner side wall of the transfer case, a third bevel gear is rotatably connected to the top of the transfer case, the bottom of the second bevel gear is meshed with the first bevel gear, and the top is meshed with the third bevel gear, and the third bevel gear is dynamically connected to the input and output ends of the travel reducer.

[0012] Furthermore, a transfer gear is provided in the transfer case and is power-connected to the second output shaft, one side of the transfer case extends to the top of the gear pump, a driving gear is provided in the gear pump, an output gear is provided in the transfer case and is power-connected to the driving gear, a speed change gear set is provided in the transfer case, an input end of the speed change gear set is meshed with the transfer gear, and an output end is meshed with the output gear.

[0013] The advantages of the present invention compared with the prior art are:

[0014] The present invention adopts a double-toothed rail type hanging rail and two independent hydraulic motors to respectively drive the travel gears to mesh and travel, and the two hydraulic motors are made to perform differential speed when turning, thereby reducing the loss of the toothed rail and the travel gear.

[0015] The present invention automatically distributes the hydraulic oil flow of the hydraulic motors on both sides for differential speed through the residual mechanical energy difference of the hydraulic oil after the hydraulic motors on both sides drive the traveling gears. No other control valve groups or external control device operation are required, and the hydraulic oil flow distribution is automatically performed.

[0016] The hydraulic differential mechanism of the present invention not only provides differential speed when turning, but also can improve the energy utilization efficiency of hydraulic oil to a certain extent when driving in a straight line, thereby increasing the power output of the hydraulic motor. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 It is a structural schematic diagram of the present invention.

[0018] Figure 2 It is a structural schematic diagram of the arc-shaped I-shaped hanging rail of the present invention.

[0019] Figure 3 It is a structural schematic diagram of the hydraulic motor of the present invention.

[0020] Figure 4 It is a schematic cross-sectional structural diagram of the hydraulic motor of the present invention.

[0021] Figure 5 It is a schematic diagram of the explosion structure of the hydraulic motor of the present invention.

[0022] Figure 6 It is a schematic structural diagram of a transfer case of the present invention.

[0023] Figure 7 It is a schematic structural diagram of the gear pump of the present invention.

[0024] Figure 8 It is a structural schematic diagram of the inlet shell of the present invention.

[0025] As shown in the figure: 1. Arc-shaped I-shaped hanging rail; 2. Outer ring gear rail; 3. Inner ring gear rail; 4. Crane; 5. Hydraulic motor; 6. Gear pump; 7. Transfer case; 8. Travel reducer; 9. Travel gear; 10. Hydraulic oil inlet pipe; 11. Buffer tank; 12. Hydraulic oil outlet pipe; 13. First stator impeller; 14. First rotor impeller; 15. Second stator impeller; 16. Second rotor impeller; 17. Inlet casing; 18. Main casing; 19. Outlet 1. housing; 20. first output shaft; 21. second output shaft; 22. shaft hole; 23. annular liquid inlet; 24. overflow ring; 25. expansion channel; 26. working channel; 27. convergence channel; 28. connecting pipe; 29. ​​first bevel gear; 30. second bevel gear; 31. third bevel gear; 32. transfer gear; 33. speed change gear set; 34. output gear; 35. driving gear; 36. gear pump inlet; 37. gear pump outlet. DETAILED DESCRIPTION

[0026] The present invention is further described in detail below in conjunction with the accompanying drawings.

[0027] Combined with Figure 1 A hydraulic traveling device for underground coal mines comprises an arc-shaped I-shaped hanging rail 1, an outer ring gear rail 2, an inner ring gear rail 3, a crane 4 and a traveling gear 9. The crane 4 is slidingly suspended on the arc-shaped I-shaped hanging rail 1. Hydraulic motors 5 are symmetrically arranged on both sides of the crane 4. A transfer case 7 is arranged on the top of the hydraulic motor 5 for power connection. A traveling reducer 8 is arranged on the top of the transfer case 7 for power connection. The traveling reducer 8 is connected to the traveling gear 9 for power connection. The outer ring gear rail 2 is fixedly arranged on the top outer ring of the arc-shaped I-shaped hanging rail 1, and the inner ring gear rail 3 is fixedly arranged on the top inner ring. The traveling gears 9 on both sides of the crane 4 are respectively meshed with the outer ring gear rail 2 and the inner ring gear rail 3.

[0028] Combined with Figure 4 and attached Figure 5 The hydraulic motor 5 is composed of an inlet housing 17, a main housing 18 and an outlet housing 19 which are sleeved and fixed in sequence from top to bottom. A first rotor impeller 14 is rotatably connected in the main housing 18. The first rotor impeller 14 is provided with a hollow first output shaft 20. A second rotor impeller 16 is rotatably connected in the outlet housing 19. The second rotor impeller 16 is provided with a second output shaft 21. The second output shaft 21 passes through the first output shaft 20 and extends to above the first output shaft 20. Both the first output shaft 20 and the second output shaft 21 extend upward into the transfer case 7. The first output shaft 20 drives the travel gear 9 through the transfer case 7.

[0029] Combined with Figure 3 and attached Figure 8A buffer tank 11 is provided at the front end of the crane 4. A hydraulic oil inlet pipe 10 is provided at the bottom of the buffer tank 11 and is connected to an external monorail crane hydraulic pump station. Gear pumps 6 are symmetrically provided on both sides of the buffer tank 11. A gear pump inlet 36 is provided on one side of the gear pump 6 and a gear pump outlet 37 is provided on the other end. The gear pump outlet 37 is provided with a connecting pipe 28 and is connected to the top of the inlet housing 17. The gear pump inlet 36 is connected to the buffer tank 11, and the second output shaft 21 drives the gear pump 6 through the transfer case 7.

[0030] Each of the impeller blades is arranged to discharge the liquid downwards and deflect the hydraulic oil while rotating around the axis of the hydraulic motor 5.

[0031] The blades of the first stator impeller 13 and the first rotor impeller 14 are arranged in opposite directions of rotation, the blades of the second stator impeller 15 and the second rotor impeller 16 are arranged in opposite directions of rotation, and the blades of the first stator impeller 13 and the second stator impeller 15 are arranged in the same direction of rotation.

[0032] Combined with Figure 4 and attached Figure 5 An annular liquid inlet 23 connected to a connecting pipe 28 is provided at the top of the inlet shell 17, an expansion channel 25 matching the first stator impeller 13 is provided in the inlet shell 17, the top of the expansion channel 25 extends to the inner circle of the annular liquid inlet 23, an overflow ring 24 extending upward is provided between the expansion channel 25 and the annular liquid inlet 23, the bottom of the expansion channel 25 extends to the blades of the first stator impeller 13, a working channel 26 matching the first rotor impeller 14 and the second stator impeller 15 is provided in the main shell 18, the top of the working channel 26 is connected to the bottom of the expansion channel 25, a convergent channel 27 matching the second rotor impeller 16 is provided in the outlet shell 19, the top of the convergent channel 27 is connected to the working channel 26, and a hydraulic oil outlet pipe 12 is provided at the bottom of the outlet shell 19 to communicate with the convergent channel 27.

[0033] The second rotor impeller 16 is generally in a convergent shape that is wider at the top and narrower at the bottom. In addition to the downward discharge and swirl direction mentioned above, the blade direction also has an inward discharge direction. The swirl radius of the hydraulic oil gradually decreases from top to bottom in the convergent flow channel 27, so that the hydraulic oil in the convergent flow channel 27 can be subjected to the centripetal force of the inner wall of the convergent flow channel 27 due to the reduction in the swirl radius, thereby increasing the force on the blades of the second rotor impeller 16 to a certain extent, and then increasing the output torque of the second rotor impeller 16 to a certain extent, which can improve the hydraulic oil delivery capacity of the gear pump 6.

[0034] Combined with Figure 6 and attached Figure 7A first bevel gear 29 is provided at the bottom of the transfer case 7 and is power-connected to the first output shaft 20. A second bevel gear 30 is rotationally connected to the inner side wall of the transfer case 7. A third bevel gear 31 is rotationally connected to the top of the transfer case 7. The bottom of the second bevel gear 30 is meshed with the first bevel gear 29, and the top is meshed with the third bevel gear 31. The third bevel gear 31 is power-connected to the input and output ends of the travel reducer 8.

[0035] Combined with Figure 6 and attached Figure 7 The transfer case 7 is provided with a transfer gear 32 which is power-connected to the second output shaft 21. One side of the transfer case 7 extends to the top of the gear pump 6. The gear pump 6 is provided with a driving gear 35. The transfer case 7 is provided with an output gear 34 which is coaxially connected to the driving gear 35. The transfer case 7 is provided with a speed change gear set 33. The input end of the speed change gear set 33 is meshed with the transfer gear 32, and the output end is meshed with the output gear 34.

[0036] The transmission mechanism can realize that the first rotor impeller 14 and the second rotor impeller 16 in the hydraulic motor 5 drive the travel gear 9 and the gear pump 6 respectively.

[0037] Combined with Figure 3 and attached Figure 7 A buffer tank 11 is provided at the front end of the crane 4, and a hydraulic oil inlet pipe 10 is provided at the bottom of the buffer tank 11 to communicate with the external monorail crane hydraulic pump station. Gear pumps 6 are symmetrically provided on both sides of the buffer tank 11, and a gear pump inlet 36 is provided on one side of the gear pump 6 and a gear pump outlet 37 is provided on the other end. The gear pump outlet 37 is provided with a connecting pipe 28 to communicate with the top of the inlet shell 17, and the gear pump inlet 36 is connected to the buffer tank 11.

[0038] Reference Figure 5 and attached Figure 8 The direction of the connecting pipe 28 is in the same direction as the deflection direction of the first stator impeller 13 and is tangent to the overflow ring 24. When the hydraulic oil is pumped into the annular liquid inlet 23 through the connecting pipe 28, the annular liquid inlet 23 rotates around the rotary hydraulic motor 5 due to the direction of the connecting pipe 28, and then enters the expansion channel 25 after being deflected by the overflow ring 24. After contacting the blades of the first stator impeller 13, it is further deflected, increasing the angle of attack between the first rotor impeller 14 and the hydraulic oil, thereby increasing the torque output of the first rotor impeller 14 and improving the power of the travel gear 9.

[0039] When the rack-type monorail crane is traveling at a rack turning point, the number of teeth on the outer ring rack 2 is greater than that on the inner ring rack 3. If the monorail crane needs to travel smoothly, the running gears 9 on both sides need to have different speeds. Figure 2, the tooth number ratio of the traveling gear 9 to the outer ring rack 2 is smaller than the tooth number ratio of the traveling gear 9 to the inner ring rack 3. If the crane is regarded as fixed, the arc-shaped I-shaped hanging rail 1 can be regarded as driven by the traveling gears 9 on both sides of the device, rotating around the center of the arc-shaped I-shaped hanging rail 1. In this reference system, when the traveling gear 9 is meshed with the outer ring rack 2, the torque amplification ratio is greater than the torque amplification ratio of the traveling gear 9 to the inner ring rack 3. For the hydraulic motor 5, the first rotor impeller 14 in the hydraulic motor 5 located in the outer ring has a lower output torque, and the consumed hydraulic oil mechanical energy is less than that of the first rotor impeller 14 located in the inner ring. Therefore, when the hydraulic oil flows to the second rotor impeller 16, the residual mechanical energy of the hydraulic oil in the hydraulic motor 5 located in the outer ring is higher, which makes the second rotor impeller 16 of the outer ring 16 can obtain more rotational kinetic energy. The rotational kinetic energy of the second rotor impeller 16 drives the gear pump 6 to work through the transfer case 7. The outer ring gear pump 6 is at a higher speed. The gear pump 6 with a higher speed has a greater inlet and outlet pressure difference, which makes the hydraulic oil pressure at the outer ring gear pump inlet 36 lower than the inner ring gear pump inlet 36. Therefore, the flow rate of the hydraulic oil in the buffer tank 11 entering the outer ring gear pump inlet 36 is greater than that of the inner ring gear pump inlet 36, so that the hydraulic oil flow obtained by the outer ring gear pump 6 and the hydraulic motor 5 is greater than that of the inner ring, which plays an effect of automatic distribution of the hydraulic oil flow, so that the hydraulic motor 5 located in the outer ring outputs more power, and the traveling gear 9 located in the outer ring has a higher speed, which is convenient for the device to travel on the arc-shaped I-beam hanging rail 1.

[0040] When the rack-type monorail crane travels in a straight line, the traveling gears 9 on both sides of the device are meshed with the same linear rack, the first rotor impeller 14 consumes the same mechanical energy of the hydraulic oil, the second rotor impellers 16 in the hydraulic motors 5 on both sides obtain the same mechanical energy from the hydraulic oil, the gear pumps 6 on both sides are in the same working state, and the flow distribution of the hydraulic oil to the devices on both sides is equal, so that the hydraulic motors 5 on both sides have equal power output, and the traveling gears 9 on both sides of the device travel at the same speed.

[0041] The present invention and its implementation methods are described above, and such description is not restrictive, and the actual structure is not limited thereto. In short, if a person skilled in the art is inspired by it, and does not deviate from the purpose of the invention, and does not creatively design a structure and implementation method similar to the technical solution, they should all fall within the protection scope of the present invention.

Claims

1. A hydraulic travel device for underground coal mines, comprising an arc-shaped I-shaped hanging rail (1), an outer ring gear rail (2), an inner ring gear rail (3), a crane (4) and a travel gear (9), wherein the crane (4) is slidably suspended on the arc-shaped I-shaped hanging rail (1), hydraulic motors (5) are symmetrically arranged on both sides of the crane (4), a transfer case (7) is arranged on the top of the hydraulic motor (5) for power connection, a travel reducer (8) is arranged on the top of the transfer case (7) for power connection, and a travel reducer (8) is arranged on the top for power connection with the travel gear (9), an outer ring gear rail (2) is fixedly arranged on the top outer ring of the arc-shaped I-shaped hanging rail (1), an inner ring gear rail (3) is fixedly arranged on the top inner ring, and the travel gears (9) on both sides of the crane (4) are respectively meshed with the outer ring gear rail (2) and the inner ring gear rail (3), and characterized in that: The hydraulic motor (5) is composed of an inlet housing (17), a main housing (18) and an outlet housing (19) which are sleeved and fixed in sequence from top to bottom; a first rotor impeller (14) is rotatably connected and arranged in the main housing (18); the first rotor impeller (14) is provided with a hollow first output shaft (20); a second rotor impeller (16) is rotatably connected and arranged in the outlet housing (19); the second rotor impeller (16) is provided with a second output shaft (21); the second output shaft (21) passes through the first output shaft (20) and extends above the first output shaft (20); the first output shaft (20) and the second output shaft (21) both extend upward into a transfer case (7); the first output shaft (20) drives a travel gear (9) through the transfer case (7); The front end of the crane (4) is provided with a buffer tank (11), the bottom of the buffer tank (11) is provided with a hydraulic oil inlet pipe (10) which is connected to an external monorail crane hydraulic pump station, and gear pumps (6) are symmetrically provided on both sides of the buffer tank (11), one side of the gear pump (6) is provided with a gear pump inlet (36) and the other end is provided with a gear pump outlet (37), the gear pump outlet (37) is provided with a connecting pipe (28) which is connected to the top of the inlet housing (17), the gear pump inlet (36) is connected to the buffer tank (11), and the second output shaft (21) drives the gear pump (6) through the transfer case (7).

2. A hydraulic traveling device for underground coal mine according to claim 1, characterized in that: A first stator impeller (13) is fixedly arranged in the hydraulic motor (5), a first rotor impeller (14) is located below the first stator impeller (13), a second stator impeller (15) is arranged below the first rotor impeller (14), and a second rotor impeller (16) is located below the second stator impeller (15).

3. A hydraulic traveling device for underground coal mine according to claim 2, characterized in that: The top of the inlet housing (17) is provided with an annular liquid inlet (23) connected to the connecting pipe (28); the inlet housing (17) is provided with an expansion channel (25) matching the first stator impeller (13); the top of the expansion channel (25) is connected to the annular liquid inlet (23); the bottom extends to the blades of the first stator impeller (13); the main housing (18) is provided with a working channel (26) matching the first rotor impeller (14) and the second stator impeller (15); the top of the working channel (26) is connected to the bottom of the expansion channel (25); the outlet housing (19) is provided with a convergent channel (27) matching the second rotor impeller (16); the top of the convergent channel (27) is connected to the working channel (26); the bottom of the outlet housing (19) is provided with a hydraulic oil outlet pipe (12) connected to the convergent channel (27).

4. A hydraulic traveling device for underground coal mine according to claim 3, characterized in that: The top of the expansion channel (25) extends to the inner circle of the annular liquid inlet (23), and an overflow ring (24) extending upward is provided between the expansion channel (25) and the annular liquid inlet (23).

5. The hydraulic traveling device for underground coal mine according to claim 1, characterized in that: A first bevel gear (29) is provided at the bottom of the transfer case (7) and is dynamically connected to the first output shaft (20); a second bevel gear (30) is rotatably connected to the inner wall of the transfer case (7); a third bevel gear (31) is rotatably connected to the top of the transfer case (7); the bottom of the second bevel gear (30) meshes with the first bevel gear (29) and the top meshes with the third bevel gear (31); the third bevel gear (31) is dynamically connected to the input and output ends of the travel reducer (8).

6. The hydraulic traveling device for underground coal mine according to claim 1, characterized in that: The transfer case (7) is provided with a transfer gear (32) in power connection with the second output shaft (21); one side of the transfer case (7) extends to the top of the gear pump (6); a driving gear (35) is provided in the gear pump (6); an output gear (34) is provided in the transfer case (7) and is coaxially connected with the driving gear (35); a speed change gear set (33) is provided in the transfer case (7); an input end of the speed change gear set (33) is meshed with the transfer gear (32); and an output end of the speed change gear set (33) is meshed with the output gear (34).

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