A large torque shredder hydraulic power system

Abstract

The utility model discloses a big torque shredder hydraulic power system belongs to hydraulic control technical field, including first hydraulic motor, second hydraulic motor and cooling circulation loop, and first hydraulic motor and second hydraulic motor are connected with no. The oil inlet of no. The oil inlet of no. The oil inlet of no. The cooling oil pipe of cooling circulation loop is connected with first hydraulic motor and second hydraulic motor respectively. No. No. The first hydraulic motor and second hydraulic motor are driven by electromagnetic overflow valve, and the speed reducer and two counter-rotating cutter shafts output big torque. The first hydraulic motor and second hydraulic motor are cooled by cooling circulation loop. The utility model discloses compact structure, low in cost, and the output torque is big.

Description

Technical Field

[0001] This utility model belongs to the field of hydraulic control technology, and in particular relates to a hydraulic power system for a high-torque shredder. Background Technology

[0002] Currently, existing shredders use a motor-driven reducer directly connected to the shredder's cutter shaft to rotate, utilizing the shearing, tearing, and compressing actions of moving and fixed blades to break materials into smaller pieces. For materials with high hardness, the power of existing shredders is clearly insufficient, easily leading to jamming, overload, motor burnout, or excessive pulses causing gear damage. Constant speed and torque operation consumes a lot of electricity, and jamming under stress can easily damage the main shaft gears and bearings. Using a high-power motor requires large-scale transmission components, increasing equipment size and cost. Hydraulic power systems, on the other hand, have the advantages of compact structure, high output force, and wide speed range. Therefore, there is an urgent need to develop a hydraulic system capable of providing high torque as a power source. Utility Model Content

[0003] The purpose of this utility model is to provide a hydraulic power system for a high-torque shredder, which aims to solve the technical problems of insufficient power of existing motors, easy jamming, high power consumption at constant speed and torque, and easy damage to the main shaft gear and bearings when jamming; while high-power motor drive components have the problems of large size and high cost.

[0004] To solve the above-mentioned technical problems, the technical solution adopted by this utility model is as follows: A high-torque shredder hydraulic power system includes a first hydraulic motor and a second hydraulic motor. The first and second hydraulic motors are respectively connected to the main shaft of the shredder via reducers, and are used to drive the rollers on the two main shafts to rotate in opposite directions. The first hydraulic motor is connected to a first hydraulic pump group via a first solenoid directional valve, and the second hydraulic motor is connected to a second hydraulic pump group via a second solenoid directional valve. The oil inlets of the first and second hydraulic pump groups are respectively connected to an oil tank via oil inlet pipes. The oil return ports of the first and second solenoid directional valves are respectively connected to the oil tank. It also includes a cooling circulation loop, wherein the cooling oil pipes of the cooling circulation loop are connected to the first hydraulic motor and the second hydraulic motor respectively, and are used to cool down the first hydraulic motor and the second hydraulic motor.

[0005] Preferably, the first hydraulic pump unit includes two oil pumps I driven by motor I. A check valve I is installed on the outlet pipeline of each of the two oil pumps I. A pressure sensor I is installed at the outlet end of each of the two check valves I and is connected in parallel to a pipeline connected to the oil port of the first solenoid directional valve p. The pipeline between the check valve I and the oil pump I is connected to the oil tank via a branch line I. A solenoid relief valve I, linked to the pressure sensor I, is installed on the branch line I to release pressure through the branch line I when the pressure of the pressure sensor I exceeds the design value. Pressure gauges I are installed at the inlet ends of the two solenoid relief valves I. The second hydraulic pump unit includes two oil pumps II driven by motor II. A check valve II is installed on the outlet pipe of each of the two oil pumps II. A pressure sensor II is installed at the outlet end of each check valve II and is connected in parallel to the pipe connected to the oil port of the second solenoid directional valve p. The pipe between the check valve II and the oil pump II is connected to the oil tank via a branch line II. A solenoid relief valve II, linked to the pressure sensor II, is installed on the branch line II to release pressure through the branch line II when the pressure of the pressure sensor II exceeds the design value. Pressure gauges II are installed at the inlet ends of the two solenoid relief valves II.

[0006] Furthermore, both the first and second electromagnetic directional valves are three-position four-way directional valves, and the T-ports of the first and second electromagnetic directional valves are connected to the oil tank through return oil pipe I and return oil pipe II, respectively.

[0007] Preferably, the cooling circulation loop includes a cooling oil pump and a water cooler. The cooling oil pump is driven by a cooling motor, and the oil inlet of the cooling oil pump is connected to the oil tank through an oil inlet pipe. The oil outlet of the cooling oil pump is connected to the oil inlet of the water cooler. The first oil outlet of the water cooler is connected to a cooling oil pipe, and the second oil outlet of the water cooler is connected to the oil tank through a return oil pipe III. The cooling oil pipes are respectively connected to the cooling layers of the first hydraulic motor and the second hydraulic motor, and the cooling layer outlets of the first hydraulic motor and the second hydraulic motor are respectively connected to the oil tank through a return oil pipe IV.

[0008] Preferably, the oil pump I, oil pump II and cooling oil pump are each provided with a vibration damper on their inlet pipes, and valves are provided at the inlet end of the vibration damper and on the return oil pipe IV; and return oil filters are provided on the return oil pipes I, II and III.

[0009] Preferably, the motor I, motor II, and cooling motor are respectively connected to two oil pumps I, two oil pumps II, and cooling oil pump via bell housings and couplings.

[0010] Furthermore, both oil pump I and oil pump II are fixed displacement double gear pumps, and both motor I and motor II are variable frequency motors.

[0011] Furthermore, both the electromagnetic relief valve I and electromagnetic relief valve II are normally closed pilot-operated electromagnetic relief valves.

[0012] Furthermore, the oil tank, the first electromagnetic directional valve, the second electromagnetic directional valve, check valve I, check valve II, electromagnetic overflow valve I, electromagnetic overflow valve II, oil pump I, oil pump II, and cooling oil pump are all integrated on the bracket. The oil tank is located at the upper part of the bracket. The first electromagnetic directional valve, the second electromagnetic directional valve, check valve I, check valve II, electromagnetic overflow valve I, electromagnetic overflow valve II, oil pump I, oil pump II, and cooling oil pump are all located in the housing at the lower part of the bracket and below the oil tank. The motor I, motor II, and cooling motor are respectively located at the bottom of the bracket and on the outside of the housing.

[0013] Preferably, the top cover of the oil tank is equipped with an air filter, and the oil tank is equipped with a temperature measuring thermocouple, a level gauge and a level relay.

[0014] Compared with the prior art, the beneficial effects of this utility model are as follows: This invention connects a first hydraulic pump group and a first solenoid directional valve to a first hydraulic motor, and a second hydraulic pump group and a second solenoid directional valve to a second hydraulic pump group. Both hydraulic pump groups are powered by motors driving dual oil pumps. An solenoid relief valve adjusts the output pressure, thereby adjusting the output torque of the first and second hydraulic motors, driving two counter-rotating cutter shafts to output high torque. Simultaneously, a cooling circulation loop cools the first and second hydraulic motors. This invention allows for a more compact power equipment structure, reduced size, and lower cost, while also providing a wide speed range and high output torque, enabling flexible torque output and further improving the safety factor of the power equipment. Attached Figure Description

[0015] The accompanying drawings are provided to further understand the present invention and form part of the specification. They are used together with the embodiments of the present invention to explain the present invention and do not constitute a limitation thereof.

[0016] In the attached diagram: Figure 1 A schematic diagram of the hydraulic power system of a high-torque shredder provided for embodiments of this utility model; Figure 2 This is an external structural diagram of the hydraulic power system of the high-torque shredder in this embodiment of the present invention; Figure 3 for Figure 2 A schematic diagram of the internal structure after removing the fuel tank, the middle crossbeam of the support frame, and the front side panel of the box body; In the picture: 00-Spindle; 1-First hydraulic motor; 2-Second hydraulic motor; 3-First solenoid directional valve; 4-Second solenoid directional valve; 5-Oil tank; 6-Cooling oil pipe; 7-Motor I; 8-Oil pump I; 9-Check valve I; 10-Pressure sensor I; 11-Branch I; 12-Solenoid relief valve I; 13-Pressure gauge I; 14-Motor II; 15-Oil pump II; 16-Check valve II; 17-Pressure sensor II; 18-Branch II ; 19-Solenoid relief valve II; 20-Pressure gauge II; 21-Return oil pipe I; 22-Return oil pipe II; 23-Cooling oil pump; 24-Water cooler; 25-Cooling motor; 26-Return oil pipe III; 27-Return oil pipe IV; 28-Vibration damper; 29-Valve; 30-Return oil filter; 31-Air filter; 32-Thermocouple; 33-Level gauge; 34-Level relay; 35-Bracket; 36-Box; 37-Ladder. Detailed Implementation

[0017] To make the technical problems, technical solutions, and beneficial effects of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention. In the following detailed description of the invention, certain specific details are described in detail. However, those skilled in the art will fully understand the invention for any parts not described in detail.

[0018] Furthermore, those skilled in the art should understand that the accompanying drawings are provided only to illustrate the purpose, features, and advantages of the present invention, and are not actually drawn to scale.

[0019] Furthermore, unless the context explicitly requires it, the words "comprising," "including," and similar terms throughout the specification and claims should be interpreted as including rather than exclusive or exhaustive; that is, meaning "including but not limited to."

[0020] like Figure 1As shown in the figure, the hydraulic power system of a high-torque shredder provided by this utility model embodiment includes a first hydraulic motor 1 and a second hydraulic motor 2. The first hydraulic motor 1 and the second hydraulic motor 2 are respectively connected to the main shaft 00 of the shredder through a reducer (not shown in the figure), and the reducer generates a reduction ratio of n:1. The two main shafts drive two roller cutters to rotate in opposite directions respectively. The first hydraulic motor 1 is connected to a first hydraulic pump group through a first electromagnetic reversing valve 3, and the second hydraulic motor 2 is connected to a second hydraulic pump group through a second electromagnetic reversing valve 4. The oil inlets of the first hydraulic pump group and the second hydraulic pump group are respectively connected to an oil tank 5 through oil inlet pipes. The oil return ports of the first electromagnetic reversing valve 3 and the second electromagnetic reversing valve 4 are respectively connected to the oil tank 5. It also includes a cooling circulation loop, and the cooling oil pipes 6 of the cooling circulation loop are respectively connected to the first hydraulic motor 1 and the second hydraulic motor 2 for cooling the first hydraulic motor 1 and the second hydraulic motor 2. The first hydraulic motor 1 and the second hydraulic motor 2 drive the two main shafts to rotate through the reducer. In this embodiment, the hydraulic motor and the reducer produce a reduction ratio of 25:1, which increases the torque of the main shaft by 25 times. The two main shafts rotate in opposite directions, and the rotating main shafts drive two parallel roller cutters to shear, tear and squeeze the material to achieve the purpose of shredding.

[0021] As a preferred configuration, the first hydraulic pump unit includes two oil pumps I8 driven by motor I7. One-way valves I9 are respectively installed on the outlet pipes of the two oil pumps I8. Pressure sensors I10 are installed at the outlet ends of the two one-way valves I9 and are connected in parallel to the pipe connected to the oil port of the first solenoid directional valve 3p. The pipe between the one-way valves I9 and the oil pumps I8 is connected to the oil tank 5 via branch I11. A solenoid relief valve I12, linked to the pressure sensor I10, is installed on branch I11 to release pressure through branch I11 when the pressure of the pressure sensor I10 exceeds the design value. Pressure gauges I13 are installed at the inlet ends of the two solenoid relief valves I12. The second hydraulic pump unit includes two oil pumps II15 driven by motor II14. One-way valves II16 are respectively installed on the outlet pipes of the two oil pumps II15. Pressure sensors II17 are installed at the outlet ends of the two one-way valves II16 and are connected in parallel to the pipe connected to the oil port of the second solenoid directional valve 4p. The pipe between the one-way valves II16 and the oil pumps II15 is connected to the oil tank 5 via branch II18. A solenoid relief valve II19, linked to the pressure sensor II17, is installed on branch II18 to release pressure through branch II18 when the pressure of the pressure sensor II17 exceeds the design value. Pressure gauges II20 are installed at the inlet ends of the two solenoid relief valves II19. Power is provided by motor I7 driving dual oil pump I8 and motor II14 driving dual oil pump II15 to drive two cutter shafts 00 to rotate in opposite directions. The opening and closing of electromagnetic relief valves I12 and II19 are controlled based on the pressure values ​​set by pressure sensors I10 and II17, thus controlling the flow of oil into branch circuits I11 and II18. This, in turn, adjusts the amount of oil entering the first electromagnetic directional valve 3 and the second electromagnetic directional valve 4, ultimately adjusting the torque of the first hydraulic motor 1 and the second hydraulic motor 2. Specific pressure parameters and the forward and reverse rotation of the motors can be controlled by a controller within the shredder.

[0022] In practical applications, the two oil pumps I8 and the two oil pumps II15 can be designed to have different working pressures. Taking the No. 1 hydraulic pump set as an example, the following explanation is provided: The two oil pumps I8 are designed with a pressure of 15 MPa for the larger pump and 28 MPa for the smaller pump. When the two pumps I8 are operating simultaneously, the maximum working pressure is 15 MPa. During this operation, the motor I7's speed is controlled by a frequency converter, reaching its maximum torque at 600-1200 rpm. When the pressure signal detected by pressure sensor I10 is 15 MPa, the electromagnetic relief valve I12 corresponding to the larger pump releases pressure and does not perform any work. The smaller pump operates at its maximum torque within the 15-28 MPa pressure range, and the reducer corresponding to the first hydraulic motor 1 operates at its rated output torque of 4-6 rpm. When the pressure signal detected by pressure sensor I10 is 28 MPa, the program triggers a 3-second overload protection mechanism, causing the first hydraulic motor to reverse for 2 seconds and then rotate forward at low speed. At this time, motor I7 slows down to 600-900 rpm. When the pressure drops below 15 MPa, motor I7 accelerates again via the frequency converter, and the two oil pumps I8 operate simultaneously. The shredder using this solution can achieve a peak torque of 120,000 N·m, meeting the requirements for high torque output.

[0023] In specific design, such as Figure 1 As shown, both the first electromagnetic directional valve 3 and the second electromagnetic directional valve 4 are three-position four-way directional valves. The T-ports of the first electromagnetic directional valve 3 and the second electromagnetic directional valve 4 are connected to the oil tank 5 through return oil pipe I 21 and return oil pipe II 22, respectively. The electromagnetic directional valves control the flow direction of the hydraulic oil, thereby controlling the rotation state of the hydraulic motor.

[0024] In a specific embodiment of this utility model, the cooling circulation loop includes a cooling oil pump 23 and a water cooler 24. The cooling oil pump 23 is driven by a cooling motor 25. The oil inlet of the cooling oil pump 23 is connected to the oil tank 5 via an oil inlet pipe. The oil outlet of the cooling oil pump 23 is connected to the oil inlet of the water cooler 24. The first oil outlet of the water cooler 24 is connected to a cooling oil pipe 6, and the second oil outlet of the water cooler 24 is connected to the oil tank 5 via a return oil pipe III 26. The cooling oil pipe 6 is connected to the cooling layers of the first hydraulic motor 1 and the second hydraulic motor 2, respectively. The cooling layer outlets of the first hydraulic motor 1 and the second hydraulic motor 2 are connected to the oil tank 5 via return oil pipe IV 27, respectively. By delivering the hydraulic oil, which has undergone heat exchange and cooling with the cooling water, to the first hydraulic motor 1 and the second hydraulic motor 2 through the cooling oil pump, the two hydraulic motors can be cooled.

[0025] In specific assembly, motor I7, motor II14, and cooling motor 25 are connected to two oil pumps I8, two oil pumps II15, and cooling oil pump 23 respectively via bell housings and couplings. Vibration dampers 28 are installed on the inlet pipes of oil pumps I8, II15, and cooling oil pump 23. Valves 29, which are open-close type butterfly valves, are installed at the inlet end of each vibration damper 28 and on the return oil pipe IV27, enabling precise control of hydraulic oil flow. Return oil filters 30 are installed on return oil pipes I21, II22, and III26. Valves are also installed on the cooling oil pipe 6 connecting the first hydraulic motor 1 and the second hydraulic motor 2 to facilitate control of the cooling hydraulic oil flow. The use of vibration dampers reduces the noise of the hydraulic system, and the use of return oil filters 30 filters the return oil in the oil circuit, preventing impurities in the oil circuit from entering the oil tank and contaminating the hydraulic oil inside.

[0026] In a specific embodiment of this utility model, the cooling motor 25 has a power of 5.5KW, and both the electromagnetic relief valve I12 and electromagnetic relief valve II19 are normally closed pilot-operated electromagnetic relief valves. Meanwhile, both the oil pump I8 and oil pump II15 are fixed-displacement double gear pumps, and both the motor I7 and motor II14 are 65KW variable frequency motors. The high-power motors and fixed-displacement double gear pumps can provide significant output power.

[0027] To further optimize the above scheme, an air filter 31 is provided on the top cover of the oil tank 5, and a temperature measuring thermocouple 32, a level gauge 33 and a level relay 34 are provided inside the oil tank 5.

[0028] In specific embodiments of this utility model, such as Figure 2 , 3 As shown, the oil tank 5, the first electromagnetic directional valve 3, the second electromagnetic directional valve 4, the one-way valve I 9, the one-way valve II 16, the electromagnetic relief valve I 12, the electromagnetic relief valve II 19, the oil pump I 8, the oil pump II 15, and the cooling oil pump 23 are all integrated on the bracket 35. The oil tank 5 is located on the upper part of the bracket 35. The first electromagnetic directional valve 3, the second electromagnetic directional valve 4, the one-way valve I 9, the one-way valve II 16, the electromagnetic relief valve I 12, the electromagnetic relief valve II 19, the oil pump I 8, the oil pump II 15, and the cooling oil pump 23 are all integrated on the bracket 35. 8. Oil pump II 15 and cooling oil pump 23 are both located inside the housing 36 at the lower part of the bracket 35, and below the oil tank 5. Motor I 7, motor II 14, and cooling motor 25 are respectively located at the bottom of the bracket 35 and on the outside of the housing 36. Level gauge 33, pressure gauge I 13, pressure gauge II 20, pressure sensor I 10, and pressure sensor II 17 are respectively installed on the side wall of the housing 36 for easy observation of the hydraulic oil level and the pressure of related oil circuits. Simultaneously, a ladder 37 is installed on the side of the bracket 35 for convenient maintenance by personnel. This structure improves the integration of the power equipment, making its structure more compact, smaller in size, lighter in weight, and easier to transport.

[0029] In summary, this invention has the advantages of compact structure, small size, light weight, and low cost. The first and second hydraulic pump sets are powered by dual oil pumps driven by motors, and the output pressure is adjusted via an electromagnetic relief valve, thereby adjusting the output torque of the first and second hydraulic motors to drive two counter-rotating cutter shafts to output high torque. Simultaneously, a cooling circulation loop cools the first and second hydraulic motors. This invention enables a more compact structure, reduced size, and lower cost for the power equipment, while also providing a wide speed range and high output torque, achieving flexible output torque and further improving the safety factor of the power equipment.

[0030] Finally, it should be noted that the above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Although the utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the scope of protection of the claims of this utility model.

Claims

1. A hydraulic power system for a high-torque shredder, characterized in that: The device includes a first hydraulic motor and a second hydraulic motor. The first and second hydraulic motors are respectively connected to the main shaft of the shredder via a reducer, and are used to drive the rollers on the two main shafts to rotate in opposite directions. The first hydraulic motor is connected to a first hydraulic pump group via a first solenoid directional valve, and the second hydraulic motor is connected to a second hydraulic pump group via a second solenoid directional valve. The oil inlets of the first and second hydraulic pump groups are respectively connected to the oil tank via oil inlet pipes. The oil return ports of the first and second solenoid directional valves are respectively connected to the oil tank. It also includes a cooling circulation loop, wherein the cooling oil pipes of the cooling circulation loop are respectively connected to the first hydraulic motor and the second hydraulic motor, and are used to cool down the first hydraulic motor and the second hydraulic motor. The first hydraulic pump unit includes two oil pumps I driven by motor I. A check valve I is installed on the outlet pipeline of each of the two oil pumps I. A pressure sensor I is installed at the outlet end of each of the two check valves I and is connected in parallel to a pipeline connected to the oil port of the first solenoid directional valve p. The pipeline between the check valve I and the oil pump I is connected to the oil tank via a branch line I. A solenoid relief valve I, linked to the pressure sensor I, is installed on the branch line I to release pressure through the branch line I when the pressure of the pressure sensor I exceeds the design value. Pressure gauges I are installed at the inlet ends of the two solenoid relief valves I. The second hydraulic pump unit includes two oil pumps II driven by motor II. A check valve II is installed on the outlet pipe of each of the two oil pumps II. A pressure sensor II is installed at the outlet end of each check valve II and is connected in parallel to the pipe connected to the oil port of the second solenoid directional valve p. The pipe between the check valve II and the oil pump II is connected to the oil tank via a branch line II. A solenoid relief valve II, linked to the pressure sensor II, is installed on the branch line II to release pressure through the branch line II when the pressure of the pressure sensor II exceeds the design value. Pressure gauges II are installed at the inlet ends of the two solenoid relief valves II.

2. The hydraulic power system for a high-torque shredder according to claim 1, characterized in that: Both the first and second electromagnetic directional valves are three-position four-way directional valves. The T-ports of the first and second electromagnetic directional valves are connected to the oil tank through return oil pipe I and return oil pipe II, respectively.

3. The hydraulic power system for a high-torque shredder according to claim 2, characterized in that: The cooling circulation loop includes a cooling oil pump and a water cooler connected to a cooling water pipeline. The cooling oil pump is driven by a cooling motor. The oil inlet of the cooling oil pump is connected to the oil tank through an oil inlet pipe. The oil outlet of the cooling oil pump is connected to the oil inlet of the water cooler. The first oil outlet of the water cooler is connected to a cooling oil pipe. The second oil outlet of the water cooler is connected to the oil tank through a return oil pipe III. The cooling oil pipes are respectively connected to the cooling layers of the first hydraulic motor and the second hydraulic motor. The cooling layer outlets of the first hydraulic motor and the second hydraulic motor are respectively connected to the oil tank through a return oil pipe IV.

4. The hydraulic power system for a high-torque shredder according to claim 3, characterized in that: Vibration dampers are provided on the inlet pipes of oil pump I, oil pump II and cooling oil pump respectively, and valves are provided on the inlet end of the vibration damper and the return oil pipe IV; return oil filters are provided on the return oil pipe I, return oil pipe II and return oil pipe III.

5. The hydraulic power system for a high-torque shredder according to claim 3, characterized in that: The motor I, motor II, and cooling motor are respectively connected to two oil pumps I, two oil pumps II, and cooling oil pump via bell housings and couplings.

6. The hydraulic power system for a high-torque shredder according to claim 5, characterized in that: Both oil pump I and oil pump II are fixed displacement double gear pumps, and both motor I and motor II are variable frequency motors.

7. The hydraulic power system for a high-torque shredder according to claim 3, characterized in that: The oil tank, the first electromagnetic directional valve, the second electromagnetic directional valve, check valve I, check valve II, electromagnetic overflow valve I, electromagnetic overflow valve II, oil pump I, oil pump II, and cooling oil pump are all integrated on the bracket. The oil tank is located at the upper part of the bracket. The first electromagnetic directional valve, the second electromagnetic directional valve, check valve I, check valve II, electromagnetic overflow valve I, electromagnetic overflow valve II, oil pump I, oil pump II, and cooling oil pump are all located in the housing at the lower part of the bracket and below the oil tank. The motor I, motor II, and cooling motor are respectively located at the bottom of the bracket and on the outside of the housing.

8. The hydraulic power system for a high-torque shredder according to claim 1, characterized in that: Both electromagnetic relief valve I and electromagnetic relief valve II are normally closed pilot-operated electromagnetic relief valves.

9. A high-torque shredder hydraulic power system according to any one of claims 1-8, characterized in that: An air filter is installed on the top cover of the oil tank, and a temperature measuring thermocouple, a level gauge, and a level relay are installed inside the oil tank.

Images