A double speed drill box for a rock drill

Abstract

This disclosure proposes a dual-speed drill box for anchor bolt drilling rigs, comprising: a drill box body, a dual-speed hydraulic motor, and a switching valve assembly. When the pressure difference between the third and fourth terminals of the dual-speed hydraulic motor is not greater than a preset pressure difference, the dual-speed hydraulic motor operates in a low-speed, high-torque state; when the pressure difference between the third and fourth terminals of the dual-speed hydraulic motor is greater than the preset pressure difference, the dual-speed hydraulic motor operates in a high-speed, low-torque state. When the first and second terminals of the switching valve assembly are respectively connected to the third terminal, the pressure difference between the third and fourth terminals of the dual-speed hydraulic motor is not greater than the preset pressure difference. Furthermore, when the first and third terminals of the switching valve assembly are connected, and the second and fourth terminals are connected, the pressure difference between the third and fourth terminals of the dual-speed hydraulic motor is greater than the preset pressure difference. This dual-speed drill box for anchor bolt drilling rigs satisfies the requirements for high pre-tension torque in forward low-speed, high-torque mode and high drilling speed in reverse high-speed, low-torque mode.

Description

Technical Field

[0001] This disclosure relates to the field of dual-speed motor control technology, and more particularly to a dual-speed drill box for anchor drilling rigs. Background Technology

[0002] The construction process of integrated drill-anchor bolts involves reverse drilling and forward pre-tightening. During drilling, the bolt rotates at high speed, requiring the drill box to provide a high rotational speed, while the pre-tightening process requires the drill box to provide a high torque. In existing technologies, the displacement of the drill box motor is fixed, and its speed and torque cannot be optimally adjusted according to usage requirements. With existing single-speed motors, as the motor displacement increases, its speed decreases while its torque increases. For motors of the same model, the speed and torque are mutually restrictive; the speed and torque are the same for both forward and reverse rotation, making it impossible to simultaneously meet the requirements of high speed in forward rotation and high torque in reverse rotation.

[0003] Among them, a single-speed motor cannot simultaneously meet the requirements of high drilling speed and high preload torque. The low motor speed during drilling will increase the propulsion force of the anchor bolt drilling, increase the stress on the drill box, and reduce the reliability and life of the drill arm. Summary of the Invention

[0004] This disclosure aims to at least partially address one of the technical problems in the related art.

[0005] Therefore, the purpose of this disclosure is to provide a dual-speed drill box for anchor drilling rigs.

[0006] To achieve the above objectives, this disclosure provides a dual-speed drill box for an anchor bolt drilling rig, comprising: a drill box body; and a dual-speed hydraulic motor, wherein the power output end of the dual-speed hydraulic motor is connected to the power input end of the drill box body, and the dual-speed hydraulic motor is in a forward rotation state when the first end of the dual-speed hydraulic motor is receiving fluid and the second end is receiving fluid, and in a reverse rotation state when the first end of the dual-speed hydraulic motor is receiving fluid and the second end is receiving fluid; and when the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is not greater than a preset pressure difference, the dual-speed hydraulic motor is in a low-speed, high-torque state; and when the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is greater than the preset pressure difference, the dual-speed hydraulic motor is in a low-speed, high-torque state. The dual-speed hydraulic motor operates at high speed and low torque. A switching valve assembly is used, with its first end connected to the fourth end of the dual-speed hydraulic motor, and its second end connected to the third end of the dual-speed hydraulic motor. The third end of the switching valve assembly is connected to an oil tank, and the fourth end of the switching valve assembly is supplied with oil at a pressure greater than a first preset pressure. Specifically, when the first and second ends of the switching valve assembly are connected to the third end, the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is not greater than a preset pressure difference; and when the first and third ends of the switching valve assembly are connected, and the second and fourth ends are connected, the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is greater than the preset pressure difference.

[0007] Optionally, the dual-speed drill box further includes: a manual directional valve, the first end of which is used to introduce pressurized oil, and the second end of which is used to discharge pressurized oil; the third end of which is connected to the first end of the dual-speed hydraulic motor; and the fourth end of which is connected to the second end of the dual-speed hydraulic motor. When the first and third ends of the manual directional valve are connected, and the second and fourth ends are connected, the first end of the dual-speed hydraulic motor receives fluid and the second end receives fluid; and when the first and fourth ends of the manual directional valve are connected, and the second and third ends are connected, the first end of the dual-speed hydraulic motor receives fluid and the second end receives fluid.

[0008] Optionally, the dual-speed drill box further includes: a first balance valve, the third end of which is connected to the first end of the dual-speed hydraulic motor, and the fourth end of which is connected to the second end of the dual-speed hydraulic motor; the first end and the third end of the first balance valve are connected, and the second end and the fourth end are connected; wherein, when pressurized oil is introduced into the first end of the first balance valve and pressurized oil is discharged from the second end, the first end of the dual-speed hydraulic motor receives fluid and the second end receives fluid; and when pressurized oil is introduced into the second end of the first balance valve and pressurized oil is discharged from the first end, the first end of the dual-speed hydraulic motor receives fluid and the second end receives fluid.

[0009] Optionally, the dual-speed drill box further includes: a pressure regulating valve group, wherein the inlet end of the pressure regulating valve group is supplied with pressurized oil, and the outlet end of the pressure regulating valve group is connected to the fourth end of the switching valve group, and the pressure regulating valve group is used to adjust the oil pressure at the fourth end of the switching valve group to be not less than the first preset pressure.

[0010] Optionally, the dual-speed hydraulic motor includes: a motor section, wherein when liquid enters at the first and second ends and exits at the third end of the motor section, the motor section is in a forward rotation low-speed high-torque state; and when liquid enters at the third and second ends and exits at the first end of the motor section, the motor section is in a reverse rotation high-speed low-torque state; and a valve group section, wherein the third end of the valve group section is connected to the third end of the dual-speed hydraulic motor, and the fourth end of the valve group section is connected to the first end of the dual-speed hydraulic motor, and the fifth end of the valve group section is connected to the second end of the dual-speed hydraulic motor, wherein when the pressure difference between the first and second ends of the valve group section is greater than a preset pressure difference, the third and fifth ends of the valve group section are connected; otherwise, the fourth and fifth ends of the valve group section are connected; wherein the first end of the switching valve group is connected to the second end of the valve group section, and the second end of the switching valve group is connected to the first end of the valve group section.

[0011] Optionally, the oil drain end of the motor section is connected to the second end of the valve assembly section.

[0012] Optionally, the dual-speed drill box further includes: a shuttle valve, wherein the first and second ends of the shuttle valve are respectively connected to the first end of the dual-speed hydraulic motor, and the fourth and fifth ends of the shuttle valve are respectively connected to the second end of the dual-speed hydraulic motor, the fourth and fifth ends of the shuttle valve are respectively connected to the third end of the dual-speed hydraulic motor, and the third end of the shuttle valve is connected to the fourth end of the dual-speed hydraulic motor; wherein, when the first end of the shuttle valve is inlet and the fifth end is outlet, the third and fourth ends of the shuttle valve are connected, and the first end of the dual-speed hydraulic motor is inlet and the second end is outlet, and the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is not greater than a preset pressure difference; and, when the fifth end of the shuttle valve is inlet and the first end is outlet, the third and second ends of the shuttle valve are connected, and the first end of the dual-speed hydraulic motor is outlet and the second end is inlet, and the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is greater than a preset pressure difference.

[0013] Optionally, the dual-speed drill box further includes a sequence valve, wherein the inlet end of the sequence valve is connected to the second end of the dual-speed hydraulic motor, and the outlet end of the sequence valve is connected to the third end of the dual-speed hydraulic motor. The sequence valve is used to connect the inlet end and the outlet end when the inlet pressure of the second end of the dual-speed hydraulic motor is greater than the second preset pressure.

[0014] Optionally, the dual-speed drill box further includes: a second balancing valve, the second end of which is connected to the inlet end of the sequence valve, the third end of which is connected to the first end of the dual-speed hydraulic motor, and the fourth end of which is connected to the second end of the dual-speed hydraulic motor; the first and third ends of the second balancing valve are connected, as are the second and fourth ends; wherein, the sequence valve is used to connect the inlet and outlet ends when the inlet pressure at the second end of the second balancing valve is greater than a second preset pressure; when pressurized oil is introduced into the first end of the second balancing valve and pressurized oil is discharged from the second end, the first end of the dual-speed hydraulic motor receives fluid and the second end receives fluid, and the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is not greater than a preset pressure difference; and when pressurized oil is introduced into the second end of the second balancing valve and pressurized oil is discharged from the first end, the first end of the dual-speed hydraulic motor receives fluid and the second end receives fluid, and the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is greater than a preset pressure difference.

[0015] The technical solution provided in this disclosure may include the following beneficial effects:

[0016] The hydraulic circuit control of the switching valve group enables the switching of the state of the dual-speed hydraulic motor, thereby meeting the usage requirements of high preload torque in forward low speed high torque state and high drilling speed in reverse high speed low torque state. At the same time, the two working states can be switched freely, thereby effectively reducing the control oil circuit of the motor, thereby reducing the risk of pipe tangling, and reducing the operation steps and difficulty.

[0017] Additional aspects and advantages of this disclosure will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this disclosure. Attached Figure Description

[0018] The above and / or additional aspects and advantages of this disclosure will become apparent and readily understood from the following description of the embodiments taken in conjunction with the accompanying drawings, in which:

[0019] Figure 1 This is a schematic diagram of the oil circuit (switching valve group) of a dual-speed drill box for an anchor drilling rig according to an embodiment of this disclosure;

[0020] Figure 2 This is a schematic diagram of the oil circuit (shuttle valve) of a dual-speed drill box for an anchor drilling rig according to an embodiment of this disclosure;

[0021] Figure 3 This is a schematic diagram of the oil circuit of a dual-speed drill box for a bolt drilling rig according to an embodiment of the present disclosure (sequence valve, valve group part left position);

[0022] Figure 4 This is a schematic diagram of the oil circuit of a dual-speed drill box for a bolt drilling rig according to an embodiment of the present disclosure (sequence valve, valve group part right position);

[0023] Figure 5 This is a schematic diagram of the structure of a dual-speed hydraulic motor in a dual-speed drill box for an anchor drilling rig according to an embodiment of this disclosure;

[0024] Figure 6 This is a drilling propulsion force-speed curve proposed in one embodiment of the present disclosure;

[0025] As shown in the figure: 1. Dual-speed hydraulic motor, 11. Motor part, 12. Valve group part;

[0026] 2. Shuttle valve, 3. Sequence valve, 4. Second balancing valve, 5. Switching valve assembly, 6. Manual directional valve, 7. First balancing valve, 8. Pressure regulating valve assembly. Detailed Implementation

[0027] Embodiments of this disclosure are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are used only to explain this disclosure, and should not be construed as limiting this disclosure. Rather, embodiments of this disclosure include all variations, modifications, and equivalents falling within the spirit and scope of the appended claims.

[0028] like Figure 1 As shown in the present invention, an embodiment of the present invention proposes a dual-speed drill box for a bolt drilling rig, comprising: a drill box body, a dual-speed hydraulic motor 1, and a switching valve group 5. The power output end of the dual-speed hydraulic motor 1 is connected to the power input end of the drill box body. When the first end of the dual-speed hydraulic motor 1 is filled with fluid and the second end is drained, the dual-speed hydraulic motor 1 is in a forward rotation state. When the first end of the dual-speed hydraulic motor 1 is drained and the second end is filled with fluid, the dual-speed hydraulic motor 1 is in a reverse rotation state. When the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is not greater than a preset pressure difference, the dual-speed hydraulic motor 1 is in a low-speed, high-torque state. When the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is greater than the preset pressure difference, the dual-speed hydraulic motor 1 is in a high-speed, low-torque state. The first end of the switching valve group 5 is connected to the fourth end of the dual-speed hydraulic motor 1, and the second end of the switching valve group 5 is connected to the third end of the dual-speed hydraulic motor 1. The third end of the switching valve group 5 is connected to an oil tank, and the fourth end of the switching valve group 5 is supplied with oil at a pressure greater than a first preset pressure. Specifically, when the first and second ends of the switching valve group 5 are connected to the third end respectively, the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is not greater than the preset pressure difference; and when the first and third ends of the switching valve group 5 are connected and the second and fourth ends are connected, the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is greater than the preset pressure difference.

[0029] It is understandable that, since the power output end of the dual-speed hydraulic motor 1 is connected to the power input end of the drill box body, and the first end of the switching valve group 5 is connected to the fourth end of the dual-speed hydraulic motor 1, the second end of the switching valve group 5 is connected to the third end of the dual-speed hydraulic motor 1, the third end of the switching valve group 5 is connected to the oil tank, and the fourth end of the switching valve group 5 is supplied with oil at a pressure greater than the first preset pressure, when the first and second ends of the switching valve group 5 are respectively connected to the third end, the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is not greater than the preset pressure difference. In addition, combined with the inlet of oil at the first end and the return of oil at the second end of the dual-speed hydraulic motor 1, the dual-speed hydraulic motor 1 is in a forward rotation low-speed high-torque state. And, when the first and third ends of the switching valve group 5 are connected and the second and fourth ends are connected, the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is greater than the preset pressure difference. In addition, combined with the return of oil at the first end and the inlet of oil at the second end of the dual-speed hydraulic motor 1, the dual-speed hydraulic motor 1 is in a reverse rotation high-speed low-torque state.

[0030] Therefore, the state switching of the dual-speed hydraulic motor 1 is realized by using the hydraulic circuit control of the switching valve group 5, so as to meet the usage requirements of pre-tightening high torque in forward low speed high torque state and drilling high speed in reverse high speed low torque state. At the same time, the two working states can be switched freely, thereby effectively reducing the control oil circuit of the motor, thereby reducing the risk of pipe hanging, and reducing the operation steps and operation difficulty.

[0031] It should be noted that the dual-speed hydraulic motor 1 in this embodiment replaces the single-speed motor in the relevant embodiment, which can increase the motor speed when drilling, thereby reducing the drilling machine's thrust during drilling, and increase the torque during pre-tightening, thereby increasing the pre-tightening force of the anchor rod. Specifically, the dual-speed hydraulic motor 1 has a forward low-speed high-torque state and a reverse high-speed low-torque state. The torque in the forward low-speed high-torque state is twice that in the reverse high-speed low-torque state, and the speed in the reverse high-speed low-torque state is twice that in the forward low-speed high-torque state.

[0032] Among them, such as Figure 6 As shown, the dual-speed hydraulic motor 1 in this embodiment increases the rotational speed of the motor during drilling and reduces the propulsion force of the drill during drilling, thereby reducing wear on the drill arm and improving the reliability of the drill arm. Furthermore, the dual-speed hydraulic motor 1 in this embodiment increases the torque during pre-tightening, thereby increasing the pre-tightening force of the anchor bolt and ensuring the stable arrangement of the anchor bolt.

[0033] The dual-speed hydraulic motor 1 has a first end, a second end, a third end, and a fourth end. The first and second ends of the dual-speed hydraulic motor 1 are used for fluid inlet or return. Specifically, if the first end of the dual-speed hydraulic motor 1 can be used for fluid inlet, then the second end of the dual-speed hydraulic motor 1 is used for fluid return, and vice versa. In addition, the third end of the dual-speed hydraulic motor 1 serves as a pilot port for controlling the differential pressure using the incoming pressurized oil, and the fourth end of the dual-speed hydraulic motor 1 serves as a drain port for draining oil, which, together with the pilot port, achieves differential pressure control.

[0034] The preset differential pressure can be set according to actual needs, and there are no restrictions on it. For example, the preset differential pressure can be 6.9 bar.

[0035] The switching valve assembly 5 has a first end, a second end, a third end, and a fourth end. The switching valve assembly 5 has at least two states. One state is that the first end and the second end of the switching valve assembly 5 are both connected to the third end, and the first end and the second end of the switching valve assembly 5 are both disconnected from the fourth end. Using this state, the pressure difference between the third end and the fourth end of the dual-speed hydraulic motor 1 can be made not greater than a preset pressure difference. The other state is that the first end and the third end of the switching valve assembly 5 are connected, and the second end and the fourth end are connected. Using this state, the pressure difference between the third end and the fourth end of the dual-speed hydraulic motor 1 can be made greater than a preset pressure difference.

[0036] The specific type of switching valve group 5 can be set according to actual needs, and there is no restriction on it. For example, switching valve group 5 can be a two-position four-way valve with both manual and electric functions. Its valve core is in the initial position when it is in the right position. When the electromagnet is energized or the handle is pushed, the valve core can be pushed to the left position to work.

[0037] like Figure 1 As shown, in some embodiments, the dual-speed drill box further includes: a manual directional valve 6, the first end of which is used to introduce pressurized oil, and the second end of which is used to discharge pressurized oil; the third end of which is connected to the first end of the dual-speed hydraulic motor 1; and the fourth end of which is connected to the second end of the dual-speed hydraulic motor 1. Specifically, when the first and third ends of the manual directional valve 6 are connected, and the second and fourth ends are connected, the first end of the dual-speed hydraulic motor 1 receives fluid and the second end receives fluid; and when the first and fourth ends of the manual directional valve 6 are connected, and the second and third ends are connected, the first end of the dual-speed hydraulic motor 1 receives fluid and the second end receives fluid.

[0038] Understandably, since the first end of the manual directional valve 6 is used to introduce pressurized oil, and the second end of the manual directional valve 6 is used to discharge pressurized oil, the third end of the manual directional valve 6 is connected to the first end of the dual-speed hydraulic motor 1, and the fourth end of the manual directional valve 6 is connected to the second end of the dual-speed hydraulic motor 1, when the first and third ends of the manual directional valve 6 are connected, and the second and fourth ends are connected, the first end of the dual-speed hydraulic motor 1 receives fluid and the second end receives fluid; and when the first and fourth ends of the manual directional valve 6 are connected, and the second and third ends are connected, the first end of the dual-speed hydraulic motor 1 receives fluid and the second end receives fluid.

[0039] Therefore, by using the hydraulic circuit control of the manual reversing valve 6, the inlet and outlet hydraulic passages of the dual-speed hydraulic motor 1 can be switched. In conjunction with the switching valve group 5, the dual-speed hydraulic motor 1 can achieve a forward low-speed high-torque state and a reverse high-speed low-torque state. In turn, the forward low-speed high-torque state and the reverse high-speed low-torque state can be used to meet the requirements of high drilling speed and high pre-tightening torque.

[0040] It should be noted that the manual directional valve 6 has a first end, a second end, a third end, and a fourth end. The manual directional valve 6 has at least two states. One state is that the first and third ends of the manual directional valve 6 are connected, and the second and fourth ends are connected. In this state, the first end of the dual-speed hydraulic motor 1 can be filled with fluid, and the second end can be returned to its original position. The other state is that the first and fourth ends of the manual directional valve 6 are connected, and the second and third ends are connected. In this state, the first end of the dual-speed hydraulic motor 1 can be returned to its original position, and the second end can be filled with fluid.

[0041] When the first and third ends of the manual directional valve 6 are connected and the second and fourth ends are connected, and when the first and second ends of the switching valve group 5 are connected to the third end respectively, the dual-speed hydraulic motor 1 is in a forward rotation low-speed high-torque state. When the first and fourth ends of the manual directional valve 6 are connected and the second and third ends are connected, and when the first and third ends of the switching valve group 5 are connected and the second and fourth ends are connected, the dual-speed hydraulic motor 1 is in a reverse rotation high-speed low-torque state.

[0042] like Figure 1 As shown, in some embodiments, the dual-speed drill box further includes: a first balance valve 7, the third end of which is connected to the first end of the dual-speed hydraulic motor 1, and the fourth end of which is connected to the second end of the dual-speed hydraulic motor 1. The first and third ends of the first balance valve 7 are connected, as are the second and fourth ends. Specifically, when pressurized oil is introduced into the first end of the first balance valve 7 and pressurized oil is discharged from the second end, the first end of the dual-speed hydraulic motor 1 receives fluid and the second end receives fluid; conversely, when pressurized oil is introduced into the second end of the first balance valve 7 and pressurized oil is discharged from the first end, the first end of the dual-speed hydraulic motor 1 receives fluid and the second end receives fluid.

[0043] It is understandable that, since the third end of the first balance valve 7 is connected to the first end of the dual-speed hydraulic motor 1, and the fourth end of the first balance valve 7 is connected to the second end of the dual-speed hydraulic motor 1, the first and third ends of the first balance valve 7 are connected, and the second and fourth ends are connected, so that when the first end of the first balance valve 7 is supplied with pressurized oil and the second end is discharged with pressurized oil, the first end of the dual-speed hydraulic motor 1 is supplied with fluid and the second end is discharged with fluid; and when the second end of the first balance valve 7 is supplied with pressurized oil and the first end is discharged with pressurized oil, the first end of the dual-speed hydraulic motor 1 is discharged with fluid and the second end is supplied with fluid.

[0044] Therefore, by switching the inlet and outlet fluid passages of the first and second ends of the first balance valve 7, the inlet and outlet fluid passages of the first and second ends of the dual-speed hydraulic motor 1 can be controlled. At the same time, by utilizing the balancing effect of the first balance valve 7, the oil at the first and second ends of the dual-speed hydraulic motor 1 can be kept stable, thereby ensuring that the dual-speed hydraulic motor 1 remains stationary and does not rotate when the oil source is cut off.

[0045] It should be noted that the first balancing valve 7 has a first end, a second end, a third end and a fourth end, and the first end and the third end of the first balancing valve 7 are connected, as are the second end and the fourth end. The specific type of the first balancing valve 7 can be set according to actual needs, and there are no restrictions on it.

[0046] In this configuration, the first balance valve 7 can be arranged between the manual directional valve 6 and the dual-speed hydraulic motor 1, in conjunction with the manual directional valve 6. Specifically, the first end of the first balance valve 7 is connected to the third end of the manual directional valve 6, and the second end of the first balance valve 7 is connected to the fourth end of the manual directional valve 6.

[0047] like Figure 1 As shown, in some embodiments, the dual-speed drill box further includes: a pressure regulating valve group 8, the inlet end of which is supplied with pressurized oil, and the outlet end of the pressure regulating valve group 8 is connected to the fourth end of the switching valve group 5. The pressure regulating valve group 8 is used to adjust the oil pressure at the fourth end of the switching valve group 5 to be not less than a first preset pressure.

[0048] It is understandable that, since the pressure regulating valve group 8 is supplied with pressurized oil at its inlet end and the outlet end of the pressure regulating valve group 8 is connected to the fourth end of the switching valve group 5, the pressure regulating valve group 8 can adjust the oil pressure at the fourth end of the switching valve group 5 and adjust the oil pressure at the fourth end of the switching valve group 5 to be no less than the first preset pressure. Thus, when the first and third ends of the switching valve group 5 are connected and the second and fourth ends are connected, the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 can be greater than the preset pressure difference, thereby realizing the reverse high-speed low-torque state of the dual-speed hydraulic motor 1.

[0049] It should be noted that the pressure regulating valve group 8 is used to regulate the oil pressure at the fourth end of the switching valve group 5 to be no less than the first preset pressure. The specific type of the pressure regulating valve group 8 can be set according to actual needs and there is no restriction on it. For example, the pressure regulating valve group 8 may include: relief valve, pressure reducing valve, sequence valve 3, etc.

[0050] The first preset pressure can be set according to actual needs, and there are no restrictions on it. For example, the first preset pressure can be 40 bar, and the pressure in the oil tank can be less than 6.9 bar.

[0051] In this configuration, the inlet end of the pressure regulating valve group 8 is connected to the first end of the manual directional valve 6, and both are connected to the oil inlet pipeline.

[0052] like Figure 1 , Figure 2 , Figure 3 , Figure 4 and Figure 5As shown, in some embodiments, the dual-speed hydraulic motor 1 includes a motor section 11 and a valve assembly section 12. When liquid enters the first and second ends of the motor section 11 and exits the third end, the motor section 11 is in a forward rotation, low-speed, high-torque state. When liquid enters the third and second ends of the motor section 11 and exits the first end, the motor section 11 is in a reverse rotation, high-speed, low-torque state. The third end of the valve assembly section 12 is connected to the third end of the dual-speed hydraulic motor 1, and the fourth end of the valve assembly section 12 is connected to the first end of the dual-speed hydraulic motor 1. The fifth end of the valve assembly section 12 is connected to the second end of the dual-speed hydraulic motor 1. When the pressure difference between the first and second ends of the valve assembly section 12 is greater than a preset pressure difference, the third and fifth ends of the valve assembly section 12 are connected; otherwise, the fourth and fifth ends of the valve assembly section 12 are connected. The first end of the switching valve assembly 5 is connected to the second end of the valve assembly section 12, and the second end of the switching valve assembly 5 is connected to the first end of the valve assembly section 12.

[0053] Understandably, since the third end of valve assembly 12 is connected to the third end of dual-speed hydraulic motor 1, and the fourth end of valve assembly 12 is connected to the first end of dual-speed hydraulic motor 1, and the fifth end of valve assembly 12 is connected to the second end of dual-speed hydraulic motor 1, when the pressure difference between the first end and the second end of valve assembly 12 is not greater than a preset pressure difference, the fourth end and the fifth end of valve assembly 12 are connected, thereby allowing the fluid from the first end of dual-speed hydraulic motor 1 to enter the first end and the second end of motor assembly 11 and to exit from the third end of motor assembly 11 to the second end of dual-speed hydraulic motor 1. This achieves the forward rotation low-speed high-torque state of motor assembly 11. Conversely, when the pressure difference between the first end and the second end of valve assembly 12 is greater than a preset pressure difference, the third end and the fifth end of valve assembly 12 are connected, thereby allowing the fluid from the second end of dual-speed hydraulic motor 1 to enter the third end and the second end of motor assembly 11 and to exit from the first end of motor assembly 11 to the first end of dual-speed hydraulic motor 1. This achieves the reverse rotation high-speed low-torque state of motor assembly 11.

[0054] Thus, by using the hydraulic circuit control of the switching valve group 5, the pressure difference between the first and second ends of the valve group 12 is controlled, thereby ensuring the stable switching of the motor 11 between the forward low-speed high-torque state and the reverse high-speed low-torque state.

[0055] It should be noted that the motor part 11 is a dual-speed motor structure with a first end, a second end and a third end. When liquid enters the first end and the second end of the motor part 11 and liquid exits the third end, the motor part 11 is in a forward rotation low speed high torque state. Conversely, when liquid enters the third end and the second end of the motor part 11 and liquid exits the first end, the motor part 11 is in a reverse rotation high speed low torque state.

[0056] The motor section 11 is switched by using the pressure difference between the first and second ends of the valve group 12, which effectively simplifies the control oil circuit of the motor section 11 and ensures the high-performance and precise operation of the motor section 11.

[0057] The valve assembly 12 has a first end, a second end, a third end, a fourth end, and a fifth end, and the valve assembly 12 has at least two states. One state is that when the pressure difference between the first end and the second end of the valve assembly 12 is greater than a preset pressure difference, the third end and the fifth end of the valve assembly 12 are connected. Using this state, the motor assembly 11 can achieve a high-speed, low-torque state. The other state is that when the pressure difference between the first end and the second end of the valve assembly 12 is not greater than a preset pressure difference, the fourth end and the fifth end of the valve assembly 12 are connected. Using this state, the motor assembly 11 can achieve a low-speed, high-torque state.

[0058] The specific type of valve assembly 12 can be set according to actual needs and is not limited thereto. For example, valve assembly 12 can be a switching valve.

[0059] Among them, the valve group 12 and the motor 11 are effectively integrated into a dual-speed hydraulic motor 1 with an integral structure, and the overall state switching is realized by the hydraulic circuit control of the four ports of the dual-speed hydraulic motor 1.

[0060] like Figure 1 , Figure 2 , Figure 3 and Figure 4 As shown, in some embodiments, the oil drain end of the motor portion 11 is connected to the second end of the valve assembly portion 12.

[0061] It is understandable that, since the oil drain end of the motor part 11 is connected to the second end of the valve group part 12, the oil drain end of the motor part 11 and the second end of the valve group part 12 share the fourth end of the dual-speed hydraulic motor 1. While realizing oil drain, it works with the third end of the dual-speed hydraulic motor 1 to realize the differential pressure control between the first end and the second end of the valve group part 12.

[0062] like Figure 2As shown, in some embodiments, the dual-speed drill box further includes: a shuttle valve 2, the first and second ends of which are respectively connected to the first end of the dual-speed hydraulic motor 1, and the fourth and fifth ends of the shuttle valve 2 are respectively connected to the second end of the dual-speed hydraulic motor 1, the fourth and fifth ends of the shuttle valve 2 are respectively connected to the third end of the dual-speed hydraulic motor 1, and the third end of the shuttle valve 2 is connected to the fourth end of the dual-speed hydraulic motor 1. When fluid enters the first end of the shuttle valve 2 and returns to the fifth end, the third and fourth ends of the shuttle valve 2 are connected, causing fluid to enter the first end of the dual-speed hydraulic motor 1 and return to the second end, and the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is not greater than a preset pressure difference. Conversely, when fluid enters the fifth end of the shuttle valve 2 and returns to the first end, the third and second ends of the shuttle valve 2 are connected, causing fluid to return to the first end of the dual-speed hydraulic motor 1 and enter to the second end, and the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is greater than a preset pressure difference.

[0063] It is understandable that when the first end of the shuttle valve 2 is filled with liquid and the fifth end is returned, the first end of the dual-speed hydraulic motor 1 is filled with liquid and the second end is returned. Furthermore, based on the pressure difference between the first and fifth ends of the shuttle valve 2, the third and fourth ends of the shuttle valve 2 are connected, thereby enabling the second, third, and fourth ends of the dual-speed hydraulic motor 1 to be interconnected and all in a low-pressure state. This ensures that the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is not greater than the preset pressure difference, thus achieving the forward rotation low-speed high-torque state of the dual-speed hydraulic motor 1.

[0064] When fluid enters at the fifth end of shuttle valve 2 and returns at the first end, fluid returns at the first end of dual-speed hydraulic motor 1 and enters at the second end. Based on the pressure difference between the first and fifth ends of shuttle valve 2, the third and second ends of shuttle valve 2 are connected, thereby disconnecting the fourth end of dual-speed hydraulic motor 1 from the third and second ends respectively. This connects the fourth end of dual-speed hydraulic motor 1 to the first end and puts it in a low-pressure state (back pressure of about 10 bar). The third and second ends of dual-speed hydraulic motor 1 are in a high-pressure state, thereby achieving a pressure difference between the third and fourth ends of dual-speed hydraulic motor 1 that is greater than the preset pressure difference. This achieves the reverse high-speed low-torque state of dual-speed hydraulic motor 1.

[0065] Therefore, the state switching of the dual-speed hydraulic motor 1 is realized by using the hydraulic circuit control of the shuttle valve 2, so as to meet the use requirements of high speed and high torque for drilling by using the forward low speed and high torque state and the reverse high speed and low torque state. At the same time, the two working states can be automatically switched with the fluid inlet and outlet of the shuttle valve 2, thereby effectively reducing the control oil circuit of the motor, thereby reducing the risk of pipe hanging, and reducing the operation steps and operation difficulty.

[0066] It should be noted that, based on the fact that the second and third ends of the dual-speed hydraulic motor 1 are always in a connected state, and the shuttle valve 2 can switch the passage according to the pressure difference between the first and fifth ends, when the first end of the shuttle valve 2 is filled with liquid and the fifth end is returned, the dual-speed hydraulic motor 1 can achieve a forward rotation low speed high torque state, and when the fifth end of the shuttle valve 2 is filled with liquid and the first end is returned, the dual-speed hydraulic motor 1 can achieve a reverse rotation high speed low torque state. Thus, by using the liquid inlet and return switching of the first and fifth ends of the shuttle valve 2, the state switching of the dual-speed hydraulic motor 1 can be realized.

[0067] By utilizing the arrangement of shuttle valve 2, the control of the four ports of the dual-speed hydraulic motor 1 (the first, second, third, and fourth ports of the dual-speed hydraulic motor 1) can be converted into the control of two ports (the first and fifth ports of shuttle valve 2), thereby reducing the control oil circuit.

[0068] The shuttle valve 2 has a first end, a second end, a third end, a fourth end, and a fifth end. The shuttle valve 2 has at least two states. One state is that when liquid enters the first end of the shuttle valve 2 and liquid returns from the fifth end, the third end and the fourth end of the shuttle valve 2 are connected due to the pressure difference between the first end and the fifth end, while the third end and the second end of the shuttle valve 2 are disconnected. This state enables the dual-speed hydraulic motor 1 to achieve a forward rotation low-speed high-torque state. The other state is that when liquid enters the fifth end of the shuttle valve 2 and liquid returns from the first end, the third end and the second end of the shuttle valve 2 are connected due to the pressure difference between the first end and the fifth end, while the third end and the fourth end of the shuttle valve 2 are disconnected. This state enables the dual-speed hydraulic motor 1 to achieve a reverse rotation high-speed low-torque state.

[0069] The specific type of shuttle valve 2 can be set according to actual needs, and there are no restrictions on it.

[0070] In addition, the arrangement of shuttle valve 2 can realize the state switching of dual-speed hydraulic motor 1, and the cooperation of switching valve group 5 and manual directional valve 6 can also realize the state switching of dual-speed hydraulic motor 1. The two oil circuit structures can be isolated by valve group and operated independently. For example, the isolation of the two oil circuit structures can be realized by switching valve, etc. The state switching of dual-speed hydraulic motor 1 can be achieved independently by shuttle valve 2, or the state switching of dual-speed hydraulic motor 1 can be achieved independently by using switching valve group 5 and manual directional valve 6.

[0071] like Figure 3 and Figure 4 As shown, in some embodiments, the dual-speed drill box further includes a sequence valve 3, the inlet end of the sequence valve 3 being connected to the second end of the dual-speed hydraulic motor 1, and the outlet end of the sequence valve 3 being connected to the third end of the dual-speed hydraulic motor 1. The sequence valve 3 is used to connect the inlet end and the outlet end when the inlet pressure of the second end of the dual-speed hydraulic motor 1 is greater than the second preset pressure.

[0072] It is understandable that, since the inlet end of the sequence valve 3 is connected to the second end of the dual-speed hydraulic motor 1, and the outlet end of the sequence valve 3 is connected to the third end of the dual-speed hydraulic motor 1, when the first end of the dual-speed hydraulic motor 1 is receiving fluid and the second end is receiving fluid, the sequence valve 3 is in the open state due to the low return pressure. This results in the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 not exceeding the preset pressure difference, thus achieving the forward rotation low-speed high-torque state of the dual-speed hydraulic motor 1. Conversely, when the first end of the dual-speed hydraulic motor 1 is receiving fluid and the second end is receiving fluid, the sequence valve 3 is in the open state due to the high inlet pressure. This results in the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 exceeding the preset pressure difference, thus achieving the reverse rotation high-speed low-torque state of the dual-speed hydraulic motor 1.

[0073] Therefore, the state switching of the dual-speed hydraulic motor 1 is realized by using the hydraulic circuit control of the sequence valve 3, so as to meet the use requirements of high speed and high torque for drilling by using the forward low speed and high torque state and the reverse high speed and low torque state. At the same time, the two working states can be automatically switched with the fluid inlet and outlet of the dual-speed hydraulic motor 1, thereby effectively reducing the control oil circuit of the motor, thereby reducing the risk of pipe hanging, and reducing the operation steps and operation difficulty.

[0074] It should be noted that, based on the arrangement of the sequence valve 3 at the second end of the dual-speed hydraulic motor 1, and based on the characteristics of high inlet pressure and low return pressure, when the first end of the dual-speed hydraulic motor 1 is filled with fluid and the second end is returned with fluid, the dual-speed hydraulic motor 1 can achieve a forward rotation low-speed high-torque state, and when the first end of the dual-speed hydraulic motor 1 is returned with fluid and the second end is filled with fluid, the dual-speed hydraulic motor 1 can achieve a reverse rotation high-speed low-torque state.

[0075] The sequence valve 3 has an inlet end and an outlet end. When the inlet pressure is greater than the second preset pressure, it is open in the direction from the inlet end to the outlet end. The sequence valve 3 has at least two states. One state is that when the first end of the dual-speed hydraulic motor 1 is filled with liquid and the second end is returned with liquid, the sequence valve 3 is open. Using this state, the dual-speed hydraulic motor 1 can achieve a forward rotation low speed high torque state. The other state is that when the first end of the dual-speed hydraulic motor 1 is returned with liquid and the second end is filled with liquid, the sequence valve 3 is open. Using this state, the dual-speed hydraulic motor 1 can achieve a reverse rotation high speed low torque state.

[0076] The specific type of sequence valve 3 can be set according to actual needs and is not limited thereto. The second preset pressure can be 20 bar.

[0077] In addition, the arrangement of the sequence valve 3 can realize the state switching of the dual-speed hydraulic motor 1. The combination of shuttle valve 2, switching valve group 5 and manual directional valve 6 can also realize the state switching of the dual-speed hydraulic motor 1. Similarly, the three oil circuit structures can be isolated and operated independently by valve groups. For example, the isolation of the three oil circuit structures can be realized by switching valves, etc. The state switching of the dual-speed hydraulic motor 1 can be achieved independently by using the sequence valve 3, the shuttle valve 2, or the switching valve group 5 and manual directional valve 6.

[0078] like Figure 3 and Figure 4 As shown, in some embodiments, the dual-speed drill box further includes: a second balance valve 4, the second end of which is connected to the inlet end of the sequence valve 3, the third end of which is connected to the first end of the dual-speed hydraulic motor 1, and the fourth end of which is connected to the second end of the dual-speed hydraulic motor 1. The first and third ends of the second balance valve 4 are connected, as are the second and fourth ends. Specifically, when pressurized oil is introduced into the first end of the second balance valve 4 and pressurized oil is discharged from the second end, the first end of the dual-speed hydraulic motor 1 receives fluid while the second end receives fluid, and the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is not greater than a preset pressure difference; and when pressurized oil is introduced into the second end of the second balance valve 4 and pressurized oil is discharged from the first end, the first end of the dual-speed hydraulic motor 1 receives fluid while the second end receives fluid, and the pressure difference between the third and fourth ends of the dual-speed hydraulic motor 1 is greater than a preset pressure difference.

[0079] It is understandable that, since the second end of the second balance valve 4 is connected to the inlet end of the sequence valve 3, and the third end of the second balance valve 4 is connected to the first end of the dual-speed hydraulic motor 1, and the fourth end of the second balance valve 4 is connected to the second end of the dual-speed hydraulic motor 1, the first and third ends of the second balance valve 4 are connected, and the second and fourth ends are connected, so that when pressurized oil is introduced into the first end of the second balance valve 4 and pressurized oil is discharged from the second end, the first end of the dual-speed hydraulic motor 1 receives fluid and the second end receives fluid, thereby cooperating with the disconnection of the sequence valve 3 to achieve the forward rotation low-speed high-torque state of the dual-speed hydraulic motor 1, and when pressurized oil is introduced into the second end of the second balance valve 4 and pressurized oil is discharged from the first end, the first end of the dual-speed hydraulic motor 1 receives fluid and the second end receives fluid, thereby cooperating with the conduction of the sequence valve 3 to achieve the reverse rotation high-speed low-torque state of the dual-speed hydraulic motor 1.

[0080] Therefore, by switching the inlet and outlet fluid passages of the first and second ends of the second balance valve 4, and cooperating with the opening and closing of the sequence valve 3, the state switching of the dual-speed hydraulic motor 1 can be realized. At the same time, by utilizing the balancing effect of the second balance valve 4, the oil at the first and second ends of the dual-speed hydraulic motor 1 can be kept stable, thereby ensuring that the dual-speed hydraulic motor 1 remains stationary and does not rotate when the oil source is cut off.

[0081] In addition, during anchor drilling, the drilling thrust is related to factors such as the drilling speed and motor speed. The drilling thrust is affected by the drilling speed and motor speed; the slower the drilling speed and the higher the motor speed, the smaller the drilling force. Increasing the motor's drilling speed will accelerate the drilling speed and reduce the drilling rig's thrust during drilling.

[0082] Increasing the motor speed during drilling will accelerate the drilling speed, reduce the drilling force, decrease the feed pressure of the drill arm, reduce the wear of the moving parts of the drill arm, improve the reliability and lifespan of the drill arm, and contribute to the lightweight design of the drill arm.

[0083] The construction process for integrated drill-anchor bolts involves reverse drilling and forward pre-tightening. Increasing the drilling speed reduces the drilling rig's propulsion force and accelerates drilling; increasing the pre-tightening torque increases the pre-tightening force of the bolt. Therefore, the drilling process requires the drill box to provide a higher rotational speed, and the pre-tightening process requires the drill box to provide a higher torque.

[0084] The hydraulic motor is the power unit of the drill box, and its output is mainly reflected in two aspects: torque and speed. In a hydraulic system, flow rate and pressure are two crucial parameters.

[0085] The relationship between the flow rate and speed of a hydraulic motor can be expressed by the following formula:

[0086] Q = D × n;

[0087] Flow rate Q is the volume of liquid entering the hydraulic motor per unit time (L / min), rotational speed n is the rotational speed of the hydraulic motor (r / min), and displacement D refers to the volume of liquid discharged by the hydraulic motor per revolution (L / r).

[0088] This formula shows that when the motor displacement remains constant, increasing the flow rate will lead to an increase in speed. Conversely, to increase the speed, one can increase the flow rate or decrease the displacement.

[0089] The torque of a hydraulic motor is related to its operating pressure and displacement. Ideally, the formula for calculating torque T is:

[0090]

[0091] T is torque (in N·m), and ΔP is the pressure difference across the motor (in MPa).

[0092] This formula shows that the torque of a hydraulic motor is directly proportional to its operating pressure and displacement. To increase torque, one can increase the operating pressure or increase the displacement.

[0093] The existing drill box is powered by a constant displacement motor. Due to the limitation of the system's maximum power (maximum working pressure and maximum flow rate), the speed and torque of the constant displacement motor are mutually restrictive, and it is impossible to simultaneously meet the requirements of high drilling speed and high preload torque.

[0094] To solve the above problems, the power source of the drill box will adopt the variable displacement dual-speed motor of this embodiment (with high speed and low speed. The motor speed is twice that of the low speed at high speed, and the torque output of the motor at low speed is twice that of the high speed).

[0095] The drilling process for integrated drill-anchor bolts requires a high rotational speed from the drill box, while the pre-tightening process requires a high torque from the drill box. For the integrated drill-anchor construction process, this embodiment uses a dual-speed motor design with variable displacement for the control oil circuit switching between the two speeds.

[0096] That is, the control schemes for shuttle valve 2, sequence valve 3, and switching valve group 5 in this embodiment.

[0097] It should be noted that the second balancing valve 4 has a first end, a second end, a third end and a fourth end, and the first end and the third end of the second balancing valve 4 are connected, as are the second end and the fourth end. The specific type of the second balancing valve 4 can be set according to actual needs, and there are no restrictions on it.

[0098] In the description of this disclosure, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance. Furthermore, in the description of this disclosure, unless otherwise stated, "a plurality of" means two or more.

[0099] Any process or method description in the flowchart or otherwise herein can be understood as representing a module, segment, or portion of code comprising one or more executable instructions for implementing a particular logical function or process, and the scope of preferred embodiments of this disclosure includes additional implementations in which functions may be performed not in the order shown or discussed, including substantially simultaneously or in reverse order depending on the function involved, as will be understood by those skilled in the art to which embodiments of this disclosure pertain.

[0100] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this disclosure. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0101] Although embodiments of the present disclosure have been shown and described above, it is to be understood that the above embodiments are exemplary and should not be construed as limiting the present disclosure. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present disclosure.

Claims

1. A dual-speed drill box for an anchor bolt drilling rig, characterized in that, include: Drill box body; A dual-speed hydraulic motor is provided, wherein the power output end of the dual-speed hydraulic motor is connected to the power input end of the drill box body. When the first end of the dual-speed hydraulic motor is filled with fluid and the second end is drained, the dual-speed hydraulic motor is in forward rotation. When the first end of the dual-speed hydraulic motor is drained and the second end is filled with fluid, the dual-speed hydraulic motor is in reverse rotation. When the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is not greater than a preset pressure difference, the dual-speed hydraulic motor is in low-speed, high-torque mode. When the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is greater than the preset pressure difference, the dual-speed hydraulic motor is in high-speed, low-torque mode. A switching valve assembly, wherein the first end of the switching valve assembly is connected to the fourth end of the dual-speed hydraulic motor, and the second end of the switching valve assembly is connected to the third end of the dual-speed hydraulic motor. The third end of the switching valve assembly is connected to the oil tank, and the fourth end of the switching valve assembly is supplied with oil at a pressure greater than a first preset pressure. Specifically, when the first and second ends of the switching valve group are respectively connected to the third end, the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is not greater than the preset pressure difference; and when the first and third ends of the switching valve group are connected and the second and fourth ends are connected, the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is greater than the preset pressure difference.

2. The dual-speed drill box for anchor drilling rigs according to claim 1, characterized in that, The dual-speed drill box also includes: A manual directional valve, wherein the first end of the manual directional valve is used to introduce pressurized oil, and the second end of the manual directional valve is used to discharge pressurized oil, the third end of the manual directional valve is connected to the first end of the dual-speed hydraulic motor, and the fourth end of the manual directional valve is connected to the second end of the dual-speed hydraulic motor. Specifically, when the first and third ends of the manual directional valve are connected, and the second and fourth ends are connected, the first end of the dual-speed hydraulic motor receives fluid and the second end receives fluid; and when the first and fourth ends of the manual directional valve are connected, and the second and third ends are connected, the first end of the dual-speed hydraulic motor receives fluid and the second end receives fluid.

3. The dual-speed drill box for anchor drilling rigs according to claim 1, characterized in that, The dual-speed drill box also includes: A first balance valve, wherein the third end of the first balance valve is connected to the first end of the dual-speed hydraulic motor, and the fourth end of the first balance valve is connected to the second end of the dual-speed hydraulic motor, wherein the first end and the third end of the first balance valve are connected, and the second end and the fourth end are connected. Specifically, when pressurized oil is introduced into the first end of the first balance valve and pressurized oil is discharged from the second end, the first end of the dual-speed hydraulic motor receives fluid and the second end returns fluid; and when pressurized oil is introduced into the second end of the first balance valve and pressurized oil is discharged from the first end, the first end of the dual-speed hydraulic motor returns fluid and the second end receives fluid.

4. The dual-speed drill box for anchor drilling rigs according to claim 1, characterized in that, The dual-speed drill box also includes: A pressure regulating valve assembly is provided, wherein pressurized oil is introduced into the inlet end of the pressure regulating valve assembly, and the outlet end of the pressure regulating valve assembly is connected to the fourth end of the switching valve assembly. The pressure regulating valve assembly is used to adjust the oil pressure at the fourth end of the switching valve assembly to be not less than the first preset pressure.

5. The dual-speed drill box for anchor drilling rigs according to claim 1, characterized in that, The dual-speed hydraulic motor includes: In the motor section, when liquid enters at the first and second ends and exits at the third end, the motor section is in a forward rotation low-speed high-torque state; and when liquid enters at the third and second ends and exits at the first end, the motor section is in a reverse rotation high-speed low-torque state. In the valve assembly section, the third end of the valve assembly section is connected to the third end of the dual-speed hydraulic motor, the fourth end of the valve assembly section is connected to the first end of the dual-speed hydraulic motor, and the fifth end of the valve assembly section is connected to the second end of the dual-speed hydraulic motor. When the pressure difference between the first end and the second end of the valve assembly section is greater than a preset pressure difference, the third end and the fifth end of the valve assembly section are connected; otherwise, the fourth end and the fifth end of the valve assembly section are connected. The first end of the switching valve group is connected to the second end of the valve group portion, and the second end of the switching valve group is connected to the first end of the valve group portion.

6. The dual-speed drill box for anchor drilling rigs according to claim 5, characterized in that, The oil drain end of the motor section is connected to the second end of the valve group section.

7. The dual-speed drill box for anchor drilling rigs according to claim 1, characterized in that, The dual-speed drill box also includes: A shuttle valve, wherein the first and second ends of the shuttle valve are respectively connected to the first end of the dual-speed hydraulic motor, and the fourth and fifth ends of the shuttle valve are respectively connected to the second end of the dual-speed hydraulic motor, the fourth and fifth ends of the shuttle valve are respectively connected to the third end of the dual-speed hydraulic motor, and the third end of the shuttle valve is connected to the fourth end of the dual-speed hydraulic motor. Specifically, when liquid enters at the first end of the shuttle valve and returns at the fifth end, the third and fourth ends of the shuttle valve are connected, and the first end of the dual-speed hydraulic motor enters and the second end returns, with the pressure difference between the third and fourth ends of the dual-speed hydraulic motor not exceeding a preset pressure difference; and when liquid enters at the fifth end of the shuttle valve and returns at the first end, the third and second ends of the shuttle valve are connected, and the first end of the dual-speed hydraulic motor returns and the second end enters, with the pressure difference between the third and fourth ends of the dual-speed hydraulic motor exceeding a preset pressure difference.

8. The dual-speed drill box for anchor drilling rigs according to claim 1, characterized in that, The dual-speed drill box also includes: A sequence valve is provided, wherein the inlet end of the sequence valve is connected to the second end of the dual-speed hydraulic motor, and the outlet end of the sequence valve is connected to the third end of the dual-speed hydraulic motor. The sequence valve is used to connect the inlet end and the outlet end when the inlet pressure of the second end of the dual-speed hydraulic motor is greater than a second preset pressure.

9. The dual-speed drill box for anchor drilling rigs according to claim 8, characterized in that, The dual-speed drill box also includes: The second balance valve has its second end connected to the inlet end of the sequence valve, its third end connected to the first end of the dual-speed hydraulic motor, and its fourth end connected to the second end of the dual-speed hydraulic motor. The first and third ends of the second balance valve are connected, as are the second and fourth ends. The sequence valve is used to connect the inlet and outlet ends of the sequence valve when the inlet pressure at the second end of the second balance valve is greater than the second preset pressure. When pressurized oil is introduced into the first end of the second balance valve and pressurized oil is discharged from the second end, the first end of the dual-speed hydraulic motor receives fluid and the second end receives fluid, and the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is not greater than a preset pressure difference. When pressurized oil is introduced into the second end of the second balance valve and pressurized oil is discharged from the first end, the first end of the dual-speed hydraulic motor receives fluid and the second end receives fluid, and the pressure difference between the third and fourth ends of the dual-speed hydraulic motor is greater than a preset pressure difference.

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