Double-motor multi-gear gearbox device, power head and rock drilling machine

Abstract

The utility model provides a double-motor multi-gear gearbox device which comprises a gearbox, a gear shifting device, a first hydraulic motor, a motor connection control valve block and a second hydraulic motor, and the gear shifting device is in driving connection with the gearbox and used for switching power transmission paths of all gear sets in the gearbox to achieve gear switching. The rotating directions of the first hydraulic motor and the second hydraulic motor are opposite, the output ends of the first hydraulic motor and the second hydraulic motor are in driving connection with the two ends of an input shaft in the gearbox, and the motor connection control valve block is located on one side of the gearbox and is in hydraulic connection with the first hydraulic motor and the second hydraulic motor. The hydraulic control device is used for switching the first hydraulic motor and the second hydraulic motor to be in a series connection state or a parallel connection state in a hydraulic control mode, and therefore gear switching is achieved. Through a hydraulic control double-motor connection mode and hydraulic control mechanical gear shifting, the multi-gear effect is achieved, the requirements of multiple construction working conditions and different construction rotation parameters of the power head can be met, the structure is simple, the size is small, adaptability is high, and reliability is high.

Description

Technical Field

[0001] This application relates to the field of rock drilling equipment technology, and in particular, to a dual-motor multi-gearbox device, a power head, and a rock drilling machine. Background Technology

[0002] Tunnel construction requires various procedures, including pipe roof installation, geological forecasting, core sampling, anchor bolting, grouting reinforcement, and geological improvement. Different construction conditions necessitate different requirements for parameters such as borehole diameter, depth, rotation speed, and torque. This necessitates that the actuators—power heads—on the rock drilling equipment possess the ability to adapt to diverse parameter requirements.

[0003] In drilling operations for pipe roof construction and geological forecasting, the power head typically needs to be rotated at a low speed (e.g., below 50 rpm) while possessing strong torque output capabilities (over 10,000 Nm) to ensure safety and efficiency during construction. Conversely, in geological coring drilling operations, the operational requirements change. The power head needs to drive the drill bit to rotate at a higher linear speed, often set at 800 rpm or higher, to meet the demands of rapid coring. During this process, the torque requirement is relatively reduced. This reflects the differentiated performance requirements of drilling rig power heads under different drilling scenarios.

[0004] The core component of a power head is the gearbox, which is responsible for transmitting speed and torque. To meet the operational needs of the power head, the gearbox needs to have different gears to output different speeds and achieve different rotational parameter requirements. Currently, there are three main solutions: ① Using mechanical shifting to change the transmission ratio of the gear pairs in the gearbox to achieve different speeds and torque outputs; ② Using a dual-motor or even multi-motor connection method to change the flow through each motor to achieve different speeds and torque outputs; ③ Combining mechanical shifting and multi-motor connection methods to achieve the multi-gear output characteristic of the gearbox.

[0005] However, current mechanical gear shifting technology mostly uses manual shifting, which is complex and bulky, reducing reliability and limiting application scenarios. Multi-motor connection methods use electronic control to change gears, which is not suitable for some complex working environments. This can easily lead to wire damage or even leakage accidents, thus limiting the use scenarios of the equipment or reducing the reliability of the equipment itself. Utility Model Content

[0006] This application provides a dual-motor multi-gear gearbox device to solve the technical problems of existing technologies, such as complex structure, large size, limited application scenarios, or low reliability of the equipment itself.

[0007] The technical solution adopted in this application is as follows:

[0008] A dual-motor multi-gearbox device includes a gearbox and a shifting device. The shifting device is driven and connected to the gearbox to switch the power transmission paths of each gear set in the gearbox to achieve gear shifting. It also includes a first hydraulic motor, a motor connection control valve block, and a second hydraulic motor. The first and second hydraulic motors rotate in opposite directions and their output ends are driven and connected to both ends of the input shaft in the gearbox. The motor connection control valve block is located on one side of the gearbox and is hydraulically connected to the first and second hydraulic motors respectively. It is used to switch the first and second hydraulic motors in series or parallel by hydraulic control, thereby achieving gear shifting.

[0009] Furthermore, the motor connection control valve block includes a valve body, which contains at least a first directional valve, a first check valve, a second check valve, and a second directional valve. The P port of the first directional valve is connected to a second oil port, the T port of the first directional valve is connected to a first oil port, the A port of the first directional valve is connected to the B1 port of the first hydraulic motor, and the A1 port of the first hydraulic motor is connected to the first oil port; the B port of the first directional valve is connected to the B2 port of the second hydraulic motor, and the A2 port of the second hydraulic motor is connected to the second oil port; the input end of the first check valve is connected to the second oil port, and the output end is connected to the P port of the second directional valve; the input end of the second check valve is connected to the first oil port, and the output end is connected to the P port of the second directional valve; the T port of the second directional valve is connected to the unloading port L, and the A port of the second directional valve is connected to the first pilot control port SP1 of the first directional valve. The directional control end of the second directional valve is connected to an external control device via a control interface.

[0010] Furthermore, the reversing control end of the second reversing valve is connected to the second pilot control port SP2, which is connected to an external control oil circuit. The second reversing valve is reversed through the external control oil circuit.

[0011] Furthermore, both the first and second directional valves are threaded cartridge valves, which are detachably installed on the valve body.

[0012] Furthermore, both the first hydraulic motor and the second hydraulic motor are bidirectional hydraulic motors, and both are equipped with an oil discharge port connected to the oil tank.

[0013] Furthermore, the gearbox includes a gearbox body, a gearbox cover plate, a gearbox input shaft, a gearbox output shaft, an input shaft large gear, an input shaft small gear, an output shaft large gear, and an output shaft small gear. The gearbox input shaft and gearbox output shaft are mounted on the gearbox body, and the two ends of the gearbox input shaft are respectively driven and connected to the first hydraulic motor and the second hydraulic motor. A first gear-shaped external spline is provided in the middle of the gearbox input shaft. The input shaft large gear and input shaft small gear are rotatably mounted on the gearbox input shaft through bearings and are located on both sides of the first gear-shaped external spline. The output shaft small gear and output shaft large gear are fixedly mounted on the gearbox output shaft through a flat key or spline.

[0014] Furthermore, the shifting device includes a shifting power unit, a shift lever, a shift fork, and a clutch connected in sequence. The internal spline on the clutch engages with the first gear-shaped external spline on the input shaft of the gearbox. Meanwhile, the large gear and the small gear on the input shaft are respectively provided with a second gear-shaped external spline and a third gear-shaped external spline that engage with the internal spline on the side near the gear-shaped external spline. The axial length of the clutch is greater than the axial length of the first gear-shaped external spline on the input shaft of the gearbox.

[0015] Furthermore, the shifting power device adopts a telescopic hydraulic cylinder, the output end of which is driven and connected to the shift lever, and the telescopic hydraulic cylinder is provided with a first oil port and a second oil port.

[0016] This application also provides a power head, including a power source and the aforementioned dual-motor multi-gear gearbox device, wherein the output end of the power source is drivenly connected to the input end of the dual-motor multi-gear gearbox device.

[0017] This application also provides a rock drilling machine, including the aforementioned power head.

[0018] Compared with the prior art, this application has the following advantages:

[0019] (1) This application provides a dual-motor multi-gear gearbox device. The dual-motor multi-gear gearbox device has a simple structure. By optimizing the motor position, the two hydraulic motors drive the same input shaft, which can effectively reduce the size of the gearbox and use only one-stage transmission, thereby improving the reliability of the equipment.

[0020] (2) This application achieves four speed outputs of the gearbox through a hydraulic dual-motor connection and hydraulic mechanical shifting, which meets the various working conditions of the gearbox in actual working conditions.

[0021] (3) This application provides a motor connection control valve block that enables the series-parallel switching of motors. It is installed on one side of the gearbox. It has a simple and compact structure, is lightweight, and effectively reduces the limitations of harsh working environments on its application scenarios by controlling the operation of the valve block through hydraulics.

[0022] In addition to the purposes, features, and advantages described above, this application has other purposes, features, and advantages. The application will now be described in further detail with reference to the accompanying drawings. Attached Figure Description

[0023] The accompanying drawings, which form part of this application, are used to provide a further understanding of this application. The illustrative embodiments and descriptions of this application are used to explain this application and do not constitute an undue limitation of this application. In the drawings:

[0024] Figure 1 This is a schematic diagram of the structure of a dual-motor multi-gearbox device according to a preferred embodiment of this application.

[0025] Figure 2 This is a schematic diagram of the motor control valve block structure according to a preferred embodiment of this application.

[0026] Figure 3 This is a schematic diagram of the hydraulic principle of the motor control valve block according to a preferred embodiment of this application.

[0027] Figure 4 This is a schematic diagram of the gearbox shift transmission structure according to a preferred embodiment of this application.

[0028] In the diagram: 1. Gearbox housing; 2. Gearbox housing cover; 3. First hydraulic motor; 4. Gearbox input shaft; 4.1. First gear-shaped external spline; 5. Gearbox output shaft; 6. Input shaft large gear; 6.1. Second gear-shaped external spline; 7. Input shaft small gear; 7.1. Third gear-shaped external spline; 8. Output shaft large gear; 9. Output shaft small gear; 10. Needle roller bearing; 11. Shifting device; 11.1. Clutch; 11.1 11.1 Internal spline; 11.2 Shift fork; 11.3 Shift lever; 11.4 Telescopic cylinder; 11.4.1 First oil port; 11.4.2 Second oil port; 12. Motor connection control valve block; 12.1 Valve body; 12.2 First directional valve; 12.3 First check valve; 12.4 Second check valve; 12.5 Second directional valve; 13. Second hydraulic motor; 14. First oil port; 15. Second oil port. Detailed Implementation

[0029] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0030] Reference Figure 1 A preferred embodiment of this application provides a dual-motor multi-gearbox device, including a gearbox, a shifting device 11, a first hydraulic motor 3, a motor connection control valve block 12, and a second hydraulic motor 13. The shifting device 11 is driven and connected to the gearbox to switch the power transmission path of each gear set in the gearbox to achieve gear switching. The first hydraulic motor 3 and the second hydraulic motor 13 rotate in opposite directions and their output ends are driven and connected to both ends of the input shaft in the gearbox. The motor connection control valve block 12 is located on one side of the gearbox and is hydraulically connected to the first hydraulic motor 3 and the second hydraulic motor 13, respectively, to switch the first hydraulic motor 3 and the second hydraulic motor 13 in series or in parallel through hydraulic control, thereby achieving gear switching.

[0031] Compared with the prior art, this embodiment has the following beneficial effects:

[0032] (1) This embodiment provides a dual-motor multi-gear gearbox device. The dual-motor multi-gear gearbox device has a simple structure. By optimizing the motor position, the two hydraulic motors drive the same input shaft, which can effectively reduce the size of the gearbox and use only one-stage transmission, thereby improving the reliability of the equipment.

[0033] (2) In this embodiment, by using a hydraulic dual-motor connection method and hydraulic mechanical shifting, in the parallel working state, compared with the series state, the flow rate through a single hydraulic motor is halved, so the speed of the hydraulic motor is reduced by half and the torque is doubled. Therefore, by using a hydraulic dual-motor connection method and hydraulic mechanical shifting, the gearbox can be switched to two additional working states on the basis of the original shifting device 11, so as to achieve a multi-gear speed output effect, meet the needs of the power head for various construction conditions and different construction rotation parameters, and thus meet the various working conditions of the gearbox in actual working conditions.

[0034] (3) This embodiment provides a motor connection control valve block 12 that enables the switching of motors in series and parallel. It is installed on one side of the gearbox. It has a simple and compact structure, is lightweight, and effectively reduces the limitations of harsh working environments on its application scenarios by controlling the operation of the valve block through hydraulic means.

[0035] Preferably, such as Figure 2 and Figure 3As shown, the motor connection control valve block 12 includes a valve body 12.1. The valve body 12.1 contains at least a first directional valve 12.2, a first check valve 12.3, a second check valve 12.4, and a second directional valve 12.5. The P port of the first directional valve 12.2 is connected to the second oil port 15, the T port of the first directional valve 12.2 is connected to the first oil port 14, the A port of the first directional valve 12.2 is connected to the B1 port of the first hydraulic motor 3, and the A1 port of the first hydraulic motor 3 is connected to the first oil port 14. The B port of the first directional valve 12.2 is connected to the B2 port of the second hydraulic motor 13. The A2 port of the second hydraulic motor 13 is connected to the second oil port 15; the input end of the first check valve 12.3 is connected to the second oil port 15, and the output end is connected to the P port of the second directional valve 12.5; the input end of the second check valve 12.4 is connected to the first oil port 14, and the output end is connected to the P port of the second directional valve 12.5; the T port of the second directional valve 12.5 is connected to the unloading port L, the A port of the second directional valve 12.5 is connected to the first pilot control oil port SP1 of the first directional valve 12.2, and the directional control end of the second directional valve 12.5 is connected to an external control device through a control interface.

[0036] Specifically, the reversing control end of the second reversing valve 12.5 is connected to the second pilot control port SP2, which is connected to an external control oil circuit. The second reversing valve 12.5 is reversing through the external control oil circuit.

[0037] Preferably, the first reversing valve 12.2 and the second reversing valve 12.5 are both threaded cartridge valves, which are detachably installed on the valve body 12.1 to ensure convenient installation, simple maintenance, high flexibility, and durability and reliability.

[0038] Preferably, the first hydraulic motor 3 and the second hydraulic motor 13 are both bidirectional hydraulic motors, and both are provided with an oil drain port connected to the oil tank, so as to meet the working conditions of different steering outputs.

[0039] When the second pilot control port SP2 is not open, the second directional valve 12.5 operates in the right position. High-pressure oil from the first port 14 or the second port 15 flows through the first check valve 12.3 or the second check valve 12.4 and then through the second directional valve 12.5 to the first directional valve 12.2. The pilot oil circuit of the first directional valve 12.2 is open to high-pressure oil, causing the first directional valve 12.2 to operate in the lower position. Assuming the first port 14 is the inlet, part of the high-pressure oil flows through ports A1 and B1 of the first hydraulic motor 3 to the second port 15, while another part flows through ports B2 and A2 of the second hydraulic motor 13 to the second port 15. At this time, the two hydraulic motors are in parallel. Since the output shafts of the two hydraulic motors are connected and installed at both ends of the gearbox input shaft 4, the rotation directions of the two hydraulic motors are opposite. When the second port 15 is the inlet, the oil flow direction is opposite to that when the first port 14 is the inlet, which will not be elaborated further here.

[0040] When oil is supplied to the second pilot control port SP2, the second directional valve 12.5 operates in the left position. High-pressure oil from either the first port 14 or the second port 15 cannot reach the pilot oil path of the first directional valve 12.2, which operates in the upper position. Assuming the first port 14 is the inlet, the high-pressure oil flows through ports A1 and B1 of the first hydraulic motor 3, then through port B2 of the second hydraulic motor 13, and finally back to the second port 15. At this time, the two hydraulic motors are in series. Since the output shafts of the two hydraulic motors are connected and installed at both ends of the gearbox input shaft 4, the rotation directions of the two hydraulic motors are opposite. When the second port 15 is the inlet, the oil flow direction is opposite to that when the first port 14 is the inlet, which will not be elaborated further here.

[0041] In parallel operation, compared to series operation, the flow rate through a single hydraulic motor is halved, resulting in a 50% reduction in the rotational speed of both hydraulic motors and a 100% increase in torque.

[0042] As can be seen, the above embodiments, through the hydraulic dual-motor connection method and hydraulic mechanical shifting, can realize the switching of four working states of the gearbox, achieving a multi-gear effect, which can meet the needs of various construction conditions and different construction rotation parameters of the power head.

[0043] Preferably, such as Figure 4As shown, the gearbox includes a gearbox body 1, a gearbox cover plate 2, a gearbox input shaft 4, a gearbox output shaft 5, an input shaft large gear 6, an input shaft small gear 7, an output shaft large gear 8, and an output shaft small gear 9. The gearbox input shaft 4 and the gearbox output shaft 5 are mounted on the gearbox body. The two ends of the gearbox input shaft 4 are respectively driven and connected to the first hydraulic motor 3 and the second hydraulic motor 13. A first gear-shaped external spline 4.1 is provided in the middle of the gearbox input shaft 4. The input shaft large gear 6 and the input shaft small gear 7 are rotatably mounted on the gearbox input shaft 4 through needle roller bearings 10 and are located on both sides of the first gear-shaped external spline 4.1. The output shaft small gear 9 and the output shaft large gear 8 are fixedly mounted on the gearbox output shaft 5 through a flat key or spline and rotate synchronously with the gearbox output shaft 5.

[0044] As can be seen, in this embodiment, the gearbox itself has two different gears. Gear shifting is achieved by switching between different power transmission paths of the input shaft large gear 6, input shaft small gear 7, output shaft large gear 8, and output shaft small gear 9. The first hydraulic motor 3 is mounted on the gearbox body 1, and the second hydraulic motor 13 is mounted on the gearbox cover plate 2. The two hydraulic motors are connected in series or in parallel to jointly drive the rotation of the gearbox input shaft 4, thereby obtaining the rotation of the additional two gears. Then, the rotation is transmitted to the gearbox output shaft 5 through the gear pair, and finally to the drill rod.

[0045] The input shaft large gear 6 and input shaft small gear 7 are in a state of relative rotation with the input shaft 4, and a needle roller bearing 10 is provided between them; the output shaft large gear 8 and output shaft small gear 9 are in a state of relative stationary with the output shaft 5, and the two can be connected by a flat key or spline drive.

[0046] Preferably, the shifting device 11 includes a shifting power unit, a shift lever 11.3, a shift fork 11.2, and a clutch 11.1 connected in sequence. The internal spline 11.1.1 on the clutch 11.1 engages with the first gear-shaped external spline 4.1 on the gearbox input shaft 4. At the same time, the input shaft large gear 6 and input shaft small gear 7 are respectively provided with a second gear-shaped external spline 6.1 and a third gear-shaped external spline 7.1 that engage with the internal spline 11.1.1 on the side near the gear-shaped external spline 4.1. The axial length of the clutch is greater than the axial length of the first gear-shaped external spline 4.1 on the gearbox input shaft 4.

[0047] Specifically, the shifting power device adopts a telescopic hydraulic cylinder 11.4, the output end of which is drivenly connected to the shift lever 11.3, and the telescopic hydraulic cylinder 11.4 is provided with a first oil port 11.4.1 and a second oil port 11.4.2.

[0048] In the above embodiment, the gear shifting device 11 includes a gear shift lever 11.3, a gear shift fork 11.2, a clutch 11.1, and a telescopic cylinder 11.4, wherein the clutch 11.1, the gear shift fork 11.2, and the gear shift lever 11.3 are connected together. The telescopic cylinder 11.4 is mounted on the gearbox body 1, and the gear shift lever 11.3 extends from inside the gearbox body 1 into the telescopic cylinder 11.4.

[0049] The internal spline 11.1.1 on the clutch 11.1 engages with the first gear-shaped external spline 4.1 on the gearbox input shaft 4. Simultaneously, the input shaft large gear 6 and input shaft small gear 7 have identical second gear-shaped external splines 6.1 and 7.1 on the side closest to the first gear-shaped external spline 4.1. The axial length of the clutch 11.1 is greater than the axial length of the first gear-shaped external spline 4.1 on the gearbox input shaft 4. Therefore, during the axial movement of the clutch 11.1, the internal spline 11.1.1 on the clutch 11.1 simultaneously engages with the first gear-shaped external spline 4.1 on the gearbox input shaft 4 and a certain input shaft gear, thereby connecting the gearbox input shaft 4 to a certain gear on the gearbox input shaft 4. When the gearbox input shaft 4 is connected to the input shaft large gear 6, the gearbox output shaft 5 outputs high speed and low torque; when the gearbox output shaft 4 is connected to the input shaft small gear 7, the gearbox output shaft 5 outputs low speed and high torque, thus achieving the switching between two gears.

[0050] The shift cylinder 11.4 is provided with a first oil port 11.4.1 and a second oil port 11.4.2. When the flow direction of the oil port is switched, the shift lever 11.3 can be driven to move back and forth axially, thereby driving the clutch 11.1 to move back and forth axially, changing the connection between the gearbox input shaft 4 and each input gear, and realizing hydraulic shifting.

[0051] Another preferred embodiment of this application also provides a power head, including a power source and a dual-motor multi-gear gearbox device as described in the above embodiments, wherein the output end of the power source is drivenly connected to the input end of the dual-motor multi-gear gearbox device.

[0052] Another preferred embodiment of this application provides a rock drilling machine, including the power head described in the above embodiments.

[0053] As can be seen, the above embodiments provide at least the following characteristics:

[0054] The motor connection control valve block 12 provided in this application is installed on one side of the gearbox 1. It uses a threaded cartridge valve, has a simple and compact structure, is lightweight, and effectively reduces the limitations of harsh working environments on its application scenarios by controlling the operation of the valve block through hydraulic means.

[0055] This application provides four different speed gears through dual-motor series-parallel switching and mechanical gear shifting. At the same time, the gear shifting control method is hydraulic control, which effectively reduces the limitation of its application scenarios by harsh working environments.

[0056] The gearbox of this application uses two hydraulic motors to drive the same input shaft, which effectively reduces the size of the gearbox. At the same time, the gear transmission is carried out through only one stage of gear transmission, which improves the reliability of the equipment.

[0057] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A dual-motor multi-gear gearbox device, comprising a gearbox and a shifting device (11), wherein the shifting device (11) is drivenly connected to the gearbox for switching the power transmission paths of each gear set within the gearbox to achieve gear shifting, characterized in that: It also includes a first hydraulic motor (3), a motor connection control valve block (12), and a second hydraulic motor (13). The first hydraulic motor (3) and the second hydraulic motor (13) rotate in opposite directions and their output ends are respectively driven to the two ends of the input shaft in the gearbox. The motor connection control valve block (12) is located on one side of the gearbox and is hydraulically connected to the first hydraulic motor (3) and the second hydraulic motor (13) respectively. It is used to switch the first hydraulic motor (3) and the second hydraulic motor (13) in series or in parallel through hydraulic control, thereby realizing gear switching.

2. The dual-motor multi-gear gearbox device according to claim 1, characterized in that: The motor connection control valve block (12) includes a valve body (12.1), which contains at least a first directional valve (12.2), a first check valve (12.3), a second check valve (12.4), and a second directional valve (12.5). The P port of the first directional valve (12.2) is connected to the second oil port (15), the T port of the first directional valve (12.2) is connected to the first oil port (14), the A port of the first directional valve (12.2) is connected to the B1 port of the first hydraulic motor (3), and the A1 port of the first hydraulic motor (3) is connected to the first oil port (14). The B port of the first directional valve (12.2) is connected to the second hydraulic motor (13). The B2 port of the second hydraulic motor (13) is connected to the second oil port (15); the input end of the first check valve (12.3) is connected to the second oil port (15), and the output end is connected to the P port of the second directional valve (12.5); the input end of the second check valve (12.4) is connected to the first oil port (14), and the output end is connected to the P port of the second directional valve (12.5); the T port of the second directional valve (12.5) is connected to the unloading port L, the A port of the second directional valve (12.5) is connected to the first pilot control oil port SP1 of the first directional valve (12.2), and the directional control end of the second directional valve (12.5) is connected to an external control device through a control interface.

3. The dual-motor multi-gear gearbox device according to claim 2, characterized in that: The reversing control end of the second reversing valve (12.5) is connected to the second pilot control port SP2, which is connected to an external control oil circuit. The second reversing valve (12.5) is reversing through the external control oil circuit.

4. The dual-motor multi-gear gearbox device according to claim 2, characterized in that: The first reversing valve (12.2) and the second reversing valve (12.5) are both threaded cartridge valves, which are detachably installed on the valve body (12.1).

5. The dual-motor multi-gear gearbox device according to claim 1, characterized in that: The first hydraulic motor (3) and the second hydraulic motor (13) are both bidirectional hydraulic motors, and both are provided with an oil discharge port connected to the oil tank.

6. The dual-motor multi-gear gearbox device according to claim 1, characterized in that: The gearbox includes a gearbox body (1), a gearbox cover plate (2), a gearbox input shaft (4), a gearbox output shaft (5), an input shaft large gear (6), an input shaft small gear (7), an output shaft large gear (8), and an output shaft small gear (9). The gearbox input shaft (4) and the gearbox output shaft (5) are mounted on the gearbox body. The two ends of the gearbox input shaft (4) are respectively driven and connected to the first hydraulic motor (3) and the second hydraulic motor (13). A first gear-shaped external spline (4.1) is provided in the middle of the gearbox input shaft (4). The input shaft large gear (6) and the input shaft small gear (7) are rotatably mounted on the gearbox input shaft (4) through bearings and located on both sides of the first gear-shaped external spline (4.1). The output shaft small gear (9) and the output shaft large gear (8) are fixedly mounted on the gearbox output shaft (5) through a flat key or spline.

7. The dual-motor multi-gearbox device according to claim 6, characterized in that: The shifting device (11) includes a shifting power unit, a shift lever (11.3), a shift fork (11.2), and a clutch (11.1) connected in sequence. The internal spline (11.1.1) on the clutch (11.1) engages with the first gear-shaped external spline (4.1) on the gearbox input shaft (4). Meanwhile, the input shaft large gear (6) and input shaft small gear (7) are respectively provided with a second gear-shaped external spline (6.1) and a third gear-shaped external spline (7.1) that engage with the internal spline (11.1.1) on the side near the gear-shaped external spline (4.1). The axial length of the clutch is greater than the axial length of the first gear-shaped external spline (4.1) on the gearbox input shaft (4).

8. The dual-motor multi-gear gearbox device according to claim 7, characterized in that: The shifting power device adopts a telescopic hydraulic cylinder (11.4). The output end of the telescopic hydraulic cylinder (11.4) is drivenly connected to the shift lever (11.3). The telescopic hydraulic cylinder (11.4) is provided with a first oil port (11.4.1) and a second oil port (11.4.2).

9. A power head, characterized in that: It includes a power source and a dual-motor multi-gear gearbox device as described in any one of claims 1 to 8, wherein the output end of the power source is drivenly connected to the input end of the dual-motor multi-gear gearbox device.

10. A rock drilling machine, characterized in that, Includes the power head as described in claim 9.

Images