Clamp driving and transmission system

Abstract

The invention belongs to the technical field of tools, and discloses a clamp driving and transmission system which comprises an electric driving assembly, a hydraulic driving assembly, a clamping assembly, a rotating assembly and a clamp frame, and the electric driving assembly is electrically connected with the hydraulic driving assembly, the clamping assembly and the rotating assembly. The hydraulic driving assembly is connected with the clamping assembly and the rotating assembly through the control valve set, and the clamping assembly and the rotating assembly are installed on the clamp frame. The system is compact in structure, convenient to use and low in requirement for a power source, braking kinetic energy and gravitational potential energy can be recycled, and the system has the advantages of being high in energy efficiency, good in dynamic performance, capable of achieving accurate positioning and the like.

Description

Technical Field

[0001] The present invention belongs to the technical field of tools, and particularly relates to a clamp drive and transmission system. Background Art

[0002] As an important tool widely used in industries such as metallurgy, transportation, railway, and port, a clamp is mainly used for clamping, fastening, or hoisting operations. According to the usage requirements, its layout can be divided into horizontal and vertical types. The core functions of the clamp include the opening, clamping, and rotation of the jaws. Currently, these two actions of large clamps are mainly achieved through a hydraulic system: the hydraulic cylinder is responsible for the opening and clamping of the jaws, and the hydraulic motor drives the rotation of the clamp. Both of these actions require efficient, fast, and precise positioning under the working conditions of large load, large inertia, and frequent start and stop.

[0003] However, there are many problems in the existing technologies. Under the working conditions of large load, large inertia, and high-frequency start and stop, the hydraulic cylinder and the hydraulic motor are easily affected by load fluctuations. In order to achieve the required positioning accuracy, the existing technologies generally adopt high-performance servo valves and closed-loop control methods, and at the same time adopt a constant-pressure system for oil supply to achieve rapid start. Although this method meets the performance requirements to a certain extent, it also results in high system energy consumption, poor anti-pollution ability, and the servo valve is prone to jamming problems, thus increasing the risk of system failures. In addition, long-term operation will cause the oil temperature to be too high, and a high-power cooling system needs to be configured, which not only affects production efficiency, increases system costs, but also may reduce product quality.

[0004] The patent with the patent number CN101451548A discloses a hydraulic transmission system for realizing rapid start and stop and smooth commutation of large-inertia loads. Although relatively smooth commutation, precise positioning, and rapid start and stop are achieved through the acceleration and deceleration circuits and the pressure regulation of the electro-hydraulic proportional overflow valve, during the deceleration braking process, a large amount of braking kinetic energy is dissipated ineffectively in the valve orifice of the electro-hydraulic proportional overflow valve in the form of heat, resulting in low system energy efficiency, a sharp rise in temperature, affecting heat dissipation and oil quality, and increasing the risk of system leakage.

[0005] The patent CN116221207A discloses a discrete four-chamber hydraulic cylinder system controlled by multiple solenoid valves. Although the problem of asymmetric inlet and outlet flows of the closed-loop pump control system is solved and energy recovery is achieved by using three hydraulic cylinders to form a discrete four-chamber hydraulic cylinder, improving the system energy efficiency, its system has a large volume, limited installation space, and a high-power closed-loop pump control system has a high installed power, slow dynamic response, high cost, and the positioning accuracy is not ideal.

[0006] Therefore, the present application designs a clamp drive and transmission system to solve the above technical problems. Summary of the Invention

[0007] In order to solve the above technical problems, the present invention proposes a clamp driving and transmission system to improve the operating efficiency and positioning accuracy of the clamp and reduce the energy consumption and cost of the system.

[0008] To achieve the above-mentioned objectives, the present invention provides a clamp drive and transmission system, including an electric drive component, a hydraulic drive component, a clamping component, a rotating component and a clamp frame, wherein the electric drive component is electrically connected to the hydraulic drive component, the clamping component and the rotating component, respectively, and the hydraulic drive component is connected to the clamping component and the rotating component through a control valve group, respectively, and the clamping component and the rotating component are installed on the clamp frame.

[0009] Preferably, the hydraulic drive assembly comprises a high-pressure accumulator, a medium-pressure accumulator, an oil tank and a hydraulic power unit, and the high-pressure accumulator and the medium-pressure accumulator are respectively connected to the hydraulic power unit.

[0010] Preferably, the clamping assembly includes a jaw, a jaw arm, a connecting rod, a dual-power actuator and a clamp release control valve group, the jaw is mounted on the jaw arm, one end of the connecting rod is hinged to the jaw arm, and the other end is hinged to the dual-power actuator, the dual-power actuator is electrically connected to the electric drive assembly, the a, b, and c ports of the clamp release control valve group are respectively connected to the high-pressure accumulator, the medium-pressure accumulator and the oil tank, and the d and e ports of the clamp release control valve group are respectively connected to the dual-power actuator.

[0011] Preferably, the rotating assembly includes a clamp rod, a clamp rotation hydraulic motor, a clamp rotation electric motor, a first pinion, a second pinion, a large gear and a clamp rotation control valve group, the large gear is installed on the clamp rod and is respectively connected to the clamp rotation hydraulic motor and the clamp rotation electric motor in transmission; the clamp rotation electric motor is electrically connected to the electric drive assembly, the a, b and c ports of the clamp rotation control valve group are respectively connected to the high-pressure accumulator, the medium-pressure accumulator and the oil tank, and the d and e ports of the clamp rotation control valve group are respectively connected to the inlet and outlet of the clamp rotation hydraulic motor.

[0012] Preferably, the dual-power actuator includes a screw-driven motor, a screw pair, a seal, a cylinder body and a piston rod. The screw-driven motor is arranged at the end of the cylinder body, and the screw-driven motor is electrically connected to the electric drive assembly. The output end of the screw-driven motor is transmission-connected to the screw pair, and the screw pair extends into the inner cavity of the cylinder body and is transmission-connected to the piston rod. The seal is arranged between the piston rod and the inner cavity of the cylinder body, and the seal slides in a sealed manner with the inner cavity of the cylinder body. The seal divides the inner cavity of the cylinder body into two independent sealed cavities, and the two sealed cavities are respectively connected to the d and e ports of the clamp release control valve group.

[0013] Preferably, the clamp rotating hydraulic motor and the clamp rotating electric motor are arranged in parallel. The clamp rotating hydraulic motor is connected to the first pinion gear, and the clamp rotating electric motor is connected to the second pinion gear. Both sides of the large gear are meshed and driven with the first pinion gear and the second pinion gear respectively.

[0014] Preferably, the clamp rotating hydraulic motor and the clamp rotating electric motor can be in a series form and integrated coaxially. After the clamp rotating hydraulic motor and the clamp rotating electric motor are connected in series, they are then connected to a pinion gear and drive the large gear.

[0015] Preferably, the driving forms of the electric drive assembly and the hydraulic drive assembly include any one of pure electric, hybrid, plug-in hybrid, range extender, hydrogen energy, and internal combustion engine.

[0016] Preferably, the clamp rotating electric motor and the lead screw drive motor include one of an axial flux motor and a radial flux motor, and are arranged in series or parallel by no less than one motor.

[0017] Preferably, the high-pressure accumulator and the medium-pressure accumulator include one of a bladder accumulator, a piston accumulator, and a spring accumulator. Both the high-pressure accumulator and the medium-pressure accumulator include a hydraulic accumulator group composed of no less than one hydraulic accumulator.

[0018] Compared with the prior art, the present invention has the following advantages and technical effects:

[0019] The present invention discloses a clamp drive and transmission system. The clamping assembly uses a dual-power actuator to realize the clamping and loosening of the clamp, while the rotating assembly uses two power sources, namely a clamp rotating electric motor and a clamp rotating hydraulic motor, to realize the rotation of the clamp. Both adopt the mode of dual-power drive and control of electricity and hydraulics. On the one hand, the movement of the clamp is controlled by a lead screw drive motor or a clamp rotating electric motor. Since it is a mechanical transmission, the control performance is good, the response speed is fast, there is no influence of oil pressure fluctuation and control valve dead zone, and at the same time, the throttling loss of the valve in the hydraulic system is eliminated, improving the system energy efficiency. On the other hand, the hydraulic system performs pressure matching through accumulators of different pressure levels to overcome inertial loads, so that position, speed, and force control are not interfered by inertia and external load forces, improving the positioning accuracy. At the same time, accumulators of different levels are used to meet the peak power demand, reducing the installed power of the motor, the system mass, and the power of the heat dissipation system, and reducing the system cost; the hydraulic power unit of the hydraulic drive assembly only needs to supply hydraulic medium to the accumulator as needed, separating the load from the power source, improving the bearing conditions, having a wide range of power source selection and low requirements, and reducing the system cost.

[0020] The invention has a compact structure and is convenient to use. It does not require changing the mechanical structure of the existing clamp, has low requirements for the power source, and can recycle braking kinetic energy and gravitational potential energy at the same time. It has the advantages of high system energy efficiency, good dynamic performance, and can achieve accurate positioning. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The drawings constituting a part of this application are used to provide a further understanding of this application. The schematic embodiments of this application and their descriptions are used to explain this application and do not constitute an improper limitation to this application. In the drawings:

[0022] Figure 1 is a schematic structural diagram of the clamp drive and transmission system of the present invention;

[0023] Figure 2 is a schematic diagram of the principle of the clamp drive and transmission system in the first embodiment of the present invention;

[0024] Figure 3 is a schematic structural diagram of the dual-power actuator of the present invention;

[0025] Figure 4 is a schematic diagram of the principle of the clamp loosening / clamping control valve group and the clamp rotation control valve group of the present invention;

[0026] Figure 5 is a schematic diagram of the principle of the clamp drive and transmission system in the second embodiment of the present invention;

[0027] Figure 6 is a schematic diagram of the installation and use of the clamp of the present invention;

[0028] In the figure: 1. Electric drive assembly; 2. Hydraulic drive assembly; 3. Clamping assembly; 4. Rotating assembly; 5. Clamp frame; 6. Clamp jaws; 7. Clamp arms; 8. Connecting rod; 9. Dual-power actuator; 10. Clamp loosening / clamping control valve group; 11. Clamp rod; 12. Clamp rotation hydraulic motor; 13. Clamp rotation motor; 14. First pinion gear; 15. Second pinion gear; 16. Large gear; 17. Clamp rotation control valve group; 18. High-pressure accumulator; 19. Medium-pressure accumulator; 20. Oil tank; 21. Hydraulic power unit; 22. First control valve; 23. Second control valve; 24. Third control valve; 25. Fourth control valve; 26. Fifth control valve; 27. Sixth control valve; 28. First pressure sensor; 29. Second pressure sensor; 30. Clamp; 9-1. Lead screw drive motor; 9-2. Lead screw pair; 9-3. Seal; 9-4. Cylinder block; 9-5. Piston rod. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0029] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0030] To make the above objects, features, and advantages of the present invention more obvious and understandable, the present invention will be further described in detail below in conjunction with the accompanying drawings and specific embodiments.

[0031] Embodiment 1

[0032] Referring to the attached Figure 1 、 2 As shown, this embodiment provides a clamp drive and transmission system, including: an electric drive component 1, a hydraulic drive component 2, a clamping component 3, a rotating component 4, and a clamp frame 5. The electric drive component 1 is electrically connected to the hydraulic drive component 2, the clamping component 3, and the rotating component 4 respectively. The hydraulic drive component 2 is connected to the clamping component 3 and the rotating component 4 respectively through a control valve group. The clamping component 3 and the rotating component 4 are installed on the clamp frame 5. The clamping component 3 and the rotating component 4 are respectively used to control the loosening and clamping and rotation of the clamp, and both adopt the mode of dual-power drive and control of electricity and hydraulics.

[0033] In an embodiment of the present application, the electric drive component 1 and the hydraulic drive component 2 select any one of pure electric, hybrid, plug-in hybrid, range extender, hydrogen energy, and internal combustion engine as the drive form based on actual needs.

[0034] For a further optimized solution, the hydraulic drive component 2 includes a high-pressure accumulator 18, a medium-pressure accumulator 19, an oil tank 20, and a hydraulic power unit 21. The high-pressure accumulator 18 and the medium-pressure accumulator 19 are respectively connected to the hydraulic power unit 21. The hydraulic power unit 21 replenishes oil for the high-pressure accumulator 18 and the medium-pressure accumulator 19 as needed. The load is separated from the power source, the bearing conditions are improved, the selection range of the power source is wide and the requirements are low, reducing the system cost. The high-pressure accumulator 18 and the medium-pressure accumulator 19 form a constant-pressure network for pressure matching, overcoming inertial loads, eliminating throttling losses, overcoming the interference of inertia and external load forces on position, speed, and force control, and at the same time being used to meet peak power requirements, reducing the installed power of the motor, the system mass, and the power of the heat dissipation system, and reducing the system cost.

[0035] In an embodiment of the present application, the high-pressure accumulator 18 and the medium-pressure accumulator 19 are one of a bladder accumulator, a piston accumulator, and a spring accumulator, and those skilled in the art can select according to needs.

[0036] In one embodiment of the present application, the high-pressure accumulator 18 and the medium-pressure accumulator 19 are a hydraulic accumulator or a hydraulic accumulator group composed of two or more hydraulic accumulators, which can be selected by those skilled in the art according to actual usage requirements.

[0037] In a further optimized solution, the clamping assembly 3 includes a jaw 6, a jaw arm 7, a connecting rod 8, a dual-power actuator 9, and a clamp release control valve group 10. The jaw 6 is installed on the jaw arm 7. One end of the connecting rod 8 is hinged to the jaw arm 7, and the other end is hinged to the dual-power actuator 9. The dual-power actuator 9 is electrically connected to the electric drive assembly 1 for controlling the release and clamping of the clamp. Ports a, b, and c of the clamp release control valve group 10 are respectively connected to the high-pressure accumulator 18, the medium-pressure accumulator 19, and the fuel tank 20. Ports d and e of the clamp release control valve group 10 are respectively connected to the dual-power actuator 9 to provide hydraulic power for the dual-power actuator 9, thereby driving the dual-power actuator 9 to drive the clamp to release and clamp.

[0038] In a further optimized solution, the rotating assembly 4 includes a clamp rod 11, a clamp rotating hydraulic motor 12, a clamp rotating electric motor 13, a first pinion 14, a second pinion 15, a large gear 16, and a clamp rotating control valve group 17. The large gear 16 is installed on the clamp rod 11. The clamp rotating hydraulic motor 12 is connected to the first pinion 14, and the clamp rotating electric motor 13 is connected to the second pinion 15. Both sides of the large gear 16 are meshed with the first pinion 14 and the second pinion 15 respectively. The clamp rotating electric motor 13 is electrically connected to the electric drive assembly 1 for controlling the rotation of the clamp. Ports a, b, and c of the clamp rotating control valve group 17 are respectively connected to the high-pressure accumulator 18, the medium-pressure accumulator 19, and the fuel tank 20. Ports d and e of the clamp rotating control valve group 17 are respectively connected to the inlet and outlet of the clamp rotating hydraulic motor 12 to provide hydraulic power for the clamp rotating hydraulic motor 12, thereby driving the first pinion 14 and the large gear 16 to drive the clamp to rotate. The clamp rotating hydraulic motor 12 and the clamp rotating electric motor 13 are in a parallel form. The clamp rotating hydraulic motor 12 and the clamp rotating electric motor 13 are respectively connected to the pinions and then jointly drive the large gear 16, so that the rotating assembly 4 realizes the mode of dual-power drive and control of electricity and hydraulics.

[0039] In one embodiment of the present application, the first pinion 14 and the second pinion 15 are selected according to the layout positions of the clamp rotating hydraulic motor 12 and the clamp rotating electric motor 13.

[0040] Refer to the appendix Figure 3As shown in the figure, for the further optimized solution, the dual-power actuator 9 includes a lead screw drive motor 9-1, a lead screw pair 9-2, a seal 9-3, a cylinder block 9-4, and a piston rod 9-5. The lead screw drive motor 9-1 is arranged at the end of the cylinder block 9-4 and is electrically connected to the electric drive assembly 1. The output end of the lead screw drive motor 9-1 is drivingly connected to a lead screw pair 9-2. The lead screw pair 9-2 extends into the inner cavity of the cylinder block 9-4 and is drivingly connected to the piston rod 9-5 to control the movement of the piston rod 9-5. A seal 9-3 is arranged between the piston rod 9-5 and the inner cavity of the cylinder block 9-4. The seal 9-3 seals and slides with the inner cavity of the cylinder block 9-4. The seal 9-3 divides the inner cavity of the cylinder block 9-4 into two independent sealed cavities. The two sealed cavities are respectively communicated with ports d and e of the clamp loosening and clamping control valve group 10 to control the entry and exit of the hydraulic transmission medium in different sealed cavities, so as to provide different magnitudes of acting forces in the two sealed cavities, provide power for the movement of the piston rod 9-5, and enable the clamping assembly 3 to achieve the mode of dual-power drive and control of electricity and hydraulics.

[0041] In an embodiment of the present application, the lead screw pair 9-2 is one of a trapezoidal lead screw pair, a ball screw pair, and a planetary roller screw pair.

[0042] In an embodiment of the present application, the clamp rotation motor 13 and the lead screw drive motor 9-1 are one of an axial flux motor and a radial flux motor, and can be one or more motors connected in series or in parallel, and the drive state is selected according to actual use requirements.

[0043] Refer to the attached Figure 4 As shown in the figure, both the clamp loosening and clamping control valve group 10 and the clamp rotation control valve group 17 include a first control valve 22, a second control valve 23, a third control valve 24, a fourth control valve 25, a fifth control valve 26, a sixth control valve 27, a first pressure sensor 28, and a second pressure sensor 29. Port a of the control valve group is respectively connected to the first control valve 22 and the fourth control valve 25. Port b of the control valve group is respectively connected to the second control valve 23 and the fifth control valve 26. Port c of the control valve group is respectively connected to the third control valve 24 and the sixth control valve 27. Port d of the control valve group is respectively connected to the first control valve 22, the second control valve 23, the third control valve 24, and the first pressure sensor 28. Port e of the control valve group is respectively connected to the fourth control valve 25, the fifth control valve 26, the sixth control valve 27, and the second pressure sensor 29.

[0044] In an embodiment of the present application, the above control valve is one of a switching valve and a proportional valve, and those skilled in the art can select according to requirements.

[0045] In an embodiment of the present application, when the dual-power actuator 9 is in the over-extension condition, on the one hand, the first control valve 22 or the second control valve 23 is opened, so that the high-pressure accumulator 18 or the medium-pressure accumulator 19 communicates with the sealing cavity of the dual-power actuator 9 away from the lead screw drive motor 9-1, and the sixth control valve 27 is opened, so that the fuel tank 20 communicates with the sealing cavity of the dual-power actuator 9 close to the lead screw drive motor 9-1, and the system energy is recovered through the high-pressure accumulator 18 or the medium-pressure accumulator 19; on the other hand, the piston rod 9-5 drives the lead screw drive motor 9-1 to generate electricity through the lead screw pair 9-2, and the system energy is recovered through the electric drive assembly 1.

[0046] In an embodiment of the present application, when the dual-power actuator 9 is in the over-retraction condition, on the one hand, the fourth control valve 25 or the fifth control valve 26 is opened, so that the high-pressure accumulator 18 or the medium-pressure accumulator 19 communicates with the sealing cavity of the dual-power actuator 9 close to the lead screw drive motor 9-1, and the third control valve 24 is opened, so that the fuel tank 20 communicates with the sealing cavity of the dual-power actuator 9 away from the lead screw drive motor 9-1, and the system energy is recovered through the high-pressure accumulator 18 or the medium-pressure accumulator 19; on the other hand, the piston rod 9-5 drives the lead screw drive motor 9-1 to generate electricity through the lead screw pair 9-2, and the system energy is recovered through the electric drive assembly 1.

[0047] In an embodiment of the present application, when the clamp rotation hydraulic motor 12 and the clamp rotation motor 13 are in forward deceleration braking, on the one hand, the first control valve 22 or the second control valve 23 is opened, so that the high-pressure accumulator 18 or the medium-pressure accumulator 19 communicates with the outlet of the clamp rotation hydraulic motor 12, and the sixth control valve 27 is opened, so that the fuel tank 20 communicates with the inlet of the clamp rotation hydraulic motor 12, and the system energy is recovered through the high-pressure accumulator 18 or the medium-pressure accumulator 19; on the other hand, the clamp rotation motor 13 generates electricity, and the system energy is recovered through the electric drive assembly 1.

[0048] In an embodiment of the present application, when the clamp rotation hydraulic motor 12 and the clamp rotation motor 13 are in reverse deceleration braking, on the one hand, the fourth control valve 25 or the fifth control valve 26 is opened, so that the high-pressure accumulator 18 or the medium-pressure accumulator 19 communicates with the outlet of the clamp rotation hydraulic motor 12, and the third control valve 24 is opened, so that the fuel tank 20 communicates with the inlet of the clamp rotation hydraulic motor 12, and the system energy is recovered through the high-pressure accumulator 18 or the medium-pressure accumulator 19; on the other hand, the clamp rotation motor 13 generates electricity, and the system energy is recovered through the electric drive assembly 1.

[0049] Embodiment Two

[0050] Refer to the appendix Figure 5As shown, the difference from the first embodiment is that the hydraulic power unit 21 is driven by an internal combustion engine to drive a hydraulic pump to supply oil to the high-pressure accumulator 18 and the medium-pressure accumulator 19; the clamp rotation hydraulic motor 12 and the clamp rotation electric motor 13 are in series. After the clamp rotation hydraulic motor 12 and the clamp rotation electric motor 13 are connected, they are then connected to the second pinion 15, and further drive the large gear 16 to drive the clamp to rotate.

[0051] In an embodiment of the present application, the clamp rotation hydraulic motor 12 and the clamp rotation electric motor 13 can be coaxially integrated.

[0052] In an embodiment of the present application, the arrangement order of the clamp rotation hydraulic motor 12 and the clamp rotation electric motor 13 can be adjusted according to the use requirements, and the first pinion 14 and the second pinion 15 are selected to mesh with the large gear 16 according to the arrangement positions of the clamp rotation hydraulic motor 12 and the clamp rotation electric motor 13.

[0053] Refer to the attached Figure 6 As shown, the clamp 30 of the present invention is installed at the front end of the loading and unloading machine, and is used to clamp materials and assist in performing some operations, such as turning the materials, etc.

[0054] According to two specific embodiments provided by the present invention, the following beneficial technical effects of the present invention are disclosed:

[0055] 1. The present invention uses an electric motor to replace the servo valve for controlling the movement. Since it is a mechanical transmission, it has good control performance, fast response speed, no influence of oil pressure fluctuation and control valve dead zone, and at the same time eliminates the throttling loss of the valve in the hydraulic system. The hydraulic system performs pressure matching through accumulators of different pressure levels to overcome inertial loads, so that position, speed, and force control are not interfered by inertia and external load forces, improving the positioning accuracy and system energy efficiency. At the same time, the power of the heat dissipation system is reduced, the system cost is lowered, and the electric motor and the hydraulic motor can be coaxially integrated, further improving the transmission efficiency and power density.

[0056] 2. The present invention uses accumulators of different pressure levels to meet peak power requirements, balance gravity, and overcome inertial loads, reducing the installed power of the electric motor and the system mass.

[0057] 3. The hydraulic pump of the present invention only needs to fill the accumulator with liquid as needed, the load is separated from the power source, the bearing conditions are improved, the selection range of the power source is wide and the requirements are low, reducing the system cost.

[0058] 4. The present invention converts the braking kinetic energy and gravitational potential energy of the clamp into electrical energy or hydraulic energy for storage and utilization through an electric motor and a super capacitor bank or an accumulator, further improving the system energy efficiency.

[0059] 5. The present invention does not change the original mechanical mechanism. When used for modification, only the original hydraulic cylinder needs to be replaced with the dual-power actuator in the present invention, and the hydraulic circuit and the motor in the present invention are added to the original hydraulic system, without changing the mechanical structure.

[0060] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "longitudinal", "transverse", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present invention.

[0061] The embodiments described above are only descriptions of the preferred modes of the present invention, and do not limit the scope of the present invention. Without departing from the design spirit of the present invention, various deformations and improvements made by those of ordinary skill in the art to the technical solution of the present invention should fall within the protection scope determined by the claims of the present invention.

Claims

1. A clamp driving and transmission system, comprising an electric drive assembly (1), a hydraulic drive assembly (2), a clamp assembly (3), a rotating assembly (4) and a clamp frame (5), characterized in that: The electric drive assembly (1) is electrically connected to the hydraulic drive assembly (2), the clamping assembly (3) and the rotating assembly (4) respectively; the hydraulic drive assembly (2) is connected to the clamping assembly (3) and the rotating assembly (4) respectively via a control valve group; the clamping assembly (3) and the rotating assembly (4) are mounted on the clamp frame (5).

2. The clamp driving and transmission system according to claim 1, characterized in that: The hydraulic drive assembly (2) comprises a high-pressure accumulator (18), a medium-pressure accumulator (19), an oil tank (20) and a hydraulic power unit (21); the high-pressure accumulator (18) and the medium-pressure accumulator (19) are respectively connected to the hydraulic power unit (21).

3. The clamp driving and transmission system according to claim 2, characterized in that: The clamping assembly (3) comprises a jaw (6), a jaw arm (7), a connecting rod (8), a dual-power actuator (9) and a clamp release control valve group (10), wherein the jaw (6) is mounted on the jaw arm (7), one end of the connecting rod (8) is hinged to the jaw arm (7), and the other end is hinged to the dual-power actuator (9), the dual-power actuator (9) is electrically connected to the electric drive assembly (1), ports a, b and c of the clamp release control valve group (10) are respectively connected to the high-pressure accumulator (18), the medium-pressure accumulator (19) and the oil tank (20), and ports d and e of the clamp release control valve group (10) are respectively connected to the dual-power actuator (9).

4. The clamp driving and transmission system according to claim 3, characterized in that: The rotating assembly (4) comprises a clamp rod (11), a clamp rotating hydraulic motor (12), a clamp rotating electric motor (13), a first pinion (14), a second pinion (15), a large gear (16) and a clamp rotating control valve group (17); the large gear (16) is mounted on the clamp rod (11) and is respectively connected to the clamp rotating hydraulic motor (12) and the clamp rotating electric motor (13); the clamp rotating electric motor (13) is electrically connected to the electric drive assembly (1); ports a, b and c of the clamp rotating control valve group (17) are respectively connected to the high-pressure accumulator (18), the medium-pressure accumulator (19) and the oil tank (20); ports d and e of the clamp rotating control valve group (17) are respectively connected to the inlet and outlet of the clamp rotating hydraulic motor (12).

5. The clamp driving and transmission system according to claim 4, characterized in that: The dual-power actuator (9) comprises a screw drive motor (9-1), a screw pair (9-2), a seal (9-3), a cylinder body (9-4) and a piston rod (9-5), wherein the screw drive motor (9-1) is arranged at the end of the cylinder body (9-4), the screw drive motor (9-1) is electrically connected to the electric drive component (1), the output end of the screw drive motor (9-1) is transmission-connected to the screw pair (9-2), and the screw pair (9-3) is sealed. -2) extends into the inner cavity of the cylinder body (9-4) and is in driving connection with the piston rod (9-5), the sealing member (9-3) is arranged between the piston rod (9-5) and the inner cavity of the cylinder body (9-4), the sealing member (9-3) slides in a sealing manner with the inner cavity of the cylinder body (9-4), the sealing member (9-3) divides the inner cavity of the cylinder body (9-4) into two independent sealing cavities, and the two sealing cavities are respectively connected to the d and e ports of the clamp release control valve group (10).

6. The clamp driving and transmission system according to claim 4, characterized in that: The clamp rotating hydraulic motor (12) and the clamp rotating electric motor (13) are arranged in parallel, the clamp rotating hydraulic motor (12) is connected to the first pinion (14), the clamp rotating electric motor (13) is connected to the second pinion (15), and the two sides of the large gear (16) are respectively meshed with the first pinion (14) and the second pinion (15) for transmission.

7. The clamp driving and transmission system according to claim 4, characterized in that: The clamp rotating hydraulic motor (12) and the clamp rotating electric motor (13) are arranged in series, and the clamp rotating hydraulic motor (12) and the clamp rotating electric motor (13) are coaxially integrated. The clamp rotating hydraulic motor (12) and the clamp rotating electric motor (13) are connected in series and then connected to the small gear to drive the large gear (16).

8. The clamp driving and transmission system according to claim 1, characterized in that: The driving modes of the electric drive component (1) and the hydraulic drive component (2) include any one of pure electric, hybrid, plug-in hybrid, range-extended, hydrogen energy, and internal combustion engine.

9. The clamp driving and transmission system according to claim 5, characterized in that: The clamp rotating motor (13) and the screw driving motor (9-1) include one of an axial flux motor and a radial flux motor. The clamp rotating motor (13) includes at least one motor. When there are multiple motors, the multiple motors are arranged in series or in parallel. The screw driving motor (9-1) includes at least one motor. When there are multiple motors, the multiple motors are arranged in series or in parallel.

10. The clamp driving and transmission system according to claim 2, characterized in that: The high-pressure accumulator (18) and the medium-pressure accumulator (19) include one of an airbag accumulator, a piston accumulator, and a spring accumulator, and the high-pressure accumulator (18) and the medium-pressure accumulator (19) each include a hydraulic accumulator group consisting of at least one hydraulic accumulator.

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