CN212455016U - Double-pressure hydraulic system - Google Patents
Double-pressure hydraulic system Download PDFInfo
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- CN212455016U CN212455016U CN202020830861.3U CN202020830861U CN212455016U CN 212455016 U CN212455016 U CN 212455016U CN 202020830861 U CN202020830861 U CN 202020830861U CN 212455016 U CN212455016 U CN 212455016U
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Abstract
The utility model discloses a double-pressure hydraulic system, which comprises a high-pressure pump and a low-pressure pump, wherein the high-pressure pump and the low-pressure pump are coaxially driven by a motor, the high-pressure pump and the low-pressure pump are communicated with an execution unit through a main oil supply way, and a first control valve is arranged on the main oil supply way and a communication oil way between the high-pressure pump and the low-pressure pump; the oil outlet of the high-pressure pump is provided with a multi-stage electromagnetic overflow valve, and the oil outlet of the low-pressure pump is provided with a first electromagnetic overflow valve. The utility model discloses a two pressure hydraulic system have improved the confession velocity of flow of system to improve work efficiency, the energy saving.
Description
Technical Field
The utility model relates to a hydraulic control technical field, in particular to two pressure hydraulic system.
Background
At present, an execution part of the skip car is driven by a hydraulic system, hydraulic power is generally provided by a constant power pump, the execution part comprises a hopper, a push plate, a track wheel and the like, the constant power pump is driven by a motor, and when the skip car runs empty, the flow supply speed is low, the speed of an oil cylinder is slow, the efficiency is influenced, and energy is wasted.
SUMMERY OF THE UTILITY MODEL
In view of this, the utility model provides a two hydraulic system that press has improved the confession flow velocity of system to improve work efficiency, the energy saving.
In order to achieve the above object, the utility model provides a following technical scheme:
a double-pressure hydraulic system comprises a high-pressure pump and a low-pressure pump, wherein the high-pressure pump and the low-pressure pump are coaxially driven by a motor, the high-pressure pump and the low-pressure pump are both communicated with an execution unit through a main oil supply way, and first control valves are arranged on the main oil supply way and communication oil ways between the high-pressure pump and the low-pressure pump; the oil outlet of the high-pressure pump is provided with a multi-stage electromagnetic overflow valve, and the oil outlet of the low-pressure pump is provided with a first electromagnetic overflow valve.
Optionally, the execution unit comprises a first hydraulic cylinder assembly and a second hydraulic cylinder assembly, the first hydraulic cylinder assembly and the second hydraulic cylinder assembly respectively control the working state through an electro-hydraulic directional valve, and an oil inlet of the electro-hydraulic directional valve is communicated with the main oil supply path.
Optionally, the first control valve includes a proportional throttle valve and a first check valve that are sequentially arranged, and the first check valve is arranged near the main oil supply path.
Optionally, a first pressure gauge is disposed on an oil path near an oil outlet end of the high-pressure pump and/or the low-pressure pump, and the first pressure gauge is used for detecting oil pressure of a corresponding communication oil path.
Optionally, the first pressure gauge is communicated with the oil outlet end of the high-pressure pump or the low-pressure pump through a pressure measuring hose, and the pressure measuring hose is communicated with the corresponding oil path through a pressure measuring joint.
Optionally, the execution unit further comprises a motor assembly, the motor assembly controls the working state through a proportional reversing valve, and an oil inlet of the proportional reversing valve is communicated with the main oil supply path.
Optionally, the execution unit further comprises a buffer cylinder assembly, the buffer cylinder assembly controls a working state through an electromagnetic directional valve, and an oil inlet of the electromagnetic directional valve is communicated with the main oil supply path; and a second one-way valve is arranged on an oil way close to the oil inlet of the electromagnetic directional valve.
Optionally, the cushion cylinder assembly comprises a cushion cylinder, and an oil inlet pipeline of the cushion cylinder is communicated with an accumulator.
Optionally, the oil outlet ends of the high-pressure pump and the low-pressure pump are both communicated with an oil tank through a first oil return oil path, and a first oil return oil filter is arranged on the first oil return oil path; the oil inlet ends of the high-pressure pump and the low-pressure pump are communicated with the oil tank through oil inlet oil paths, and second control valves are arranged on the oil inlet oil paths.
Optionally, the system further comprises a first air cooler for cooling the high-pressure pump and the low-pressure pump.
According to the technical scheme, the dual-pressure hydraulic system of the utility model, the low-pressure pump and the high-pressure pump form a dual-pressure driving system, and the oil outlet of the high-pressure pump is communicated with the multistage electromagnetic overflow valve, so that the high-pressure pump can have different overload pressure values, namely, the high-pressure pump has different output pressures, and the high-pressure pump has three working states of pressure relief, low pressure and high pressure; the utility model discloses an among the hydraulic system, under the low pressure user state, provide the pumping pressure jointly by low-pressure pump and high-pressure pump, under the high-pressure state, provide system's high pressure by the high-pressure pump, the utility model discloses a two pressure hydraulic system, the low-pressure pump is used with the cooperation of high-pressure pump, has improved the velocity of flow that supplies of the hydraulic oil under the system's low pressure state to improve execution unit's work efficiency, saved the time, practiced thrift the energy.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a dual-pressure hydraulic system provided by an embodiment of the present invention.
Detailed Description
The utility model discloses a two hydraulic system that press has improved the confession flow rate of system to improve work efficiency, the energy saving.
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
Referring to fig. 1, the utility model discloses a two pressure hydraulic system, including high-pressure pump 13 and low-pressure pump 8, high-pressure pump 13 and low-pressure pump 8 are by the coaxial drive of a motor 10, and high-pressure pump 13 and low-pressure pump 8 all communicate with the execution unit through main oil supply way 31, and the exit end of high-pressure pump 13 and the exit end of low-pressure pump 8 all communicate with main oil supply way 31, all are provided with first control valve on the intercommunication oil circuit between main oil supply way 31 and high-pressure pump 13, the low-pressure pump 8. The oil outlet of the high-pressure pump 13 is also provided with a multi-stage electromagnetic overflow valve 21, and the oil outlet of the low-pressure pump 8 is provided with a first electromagnetic overflow valve 20.
One end of the motor 10 is in transmission connection with the power input end of the low-pressure pump 8 through the first coupler 9, and the other end of the motor 10 is in transmission connection with the power input end of the high-pressure pump 13 through the second coupler 12, so that the high-pressure pump 13 and the low-pressure pump 8 form a dual-pump structure.
The utility model discloses a two pressure hydraulic system, low-pressure pump 8 constitute with high-pressure pump 13 and press actuating system, high-pressure pump 13's oil-out and multistage electromagnetic overflow valve 21 intercommunication to make high-pressure pump 13 can have different overload pressure values, high-pressure pump 13 has different output pressure promptly, and high-pressure pump 13 has pressure release, low pressure and the three operating condition of high pressure. When hydraulic system low pressure state, hydraulic system's low pressure service pressure is adjusted to low-pressure pump 8's pump pressure, and at this moment, hydraulic system's low pressure service pressure is also adjusted to high-pressure pump 13's pump pressure, promptly the utility model discloses an among the hydraulic system, under the low pressure service state, provide the pump pressure by low-pressure pump 8 and high-pressure pump 13 jointly, under the high-pressure state, provide system's high pressure by high-pressure pump 13, the utility model discloses a two pressure hydraulic system, low-pressure pump 8 uses with high-pressure pump 13's cooperation, has improved the velocity of flow that supplies of the hydraulic oil under the system's low pressure state to execution unit's work efficiency has been improved, has saved the time, has practiced thrift the energy.
Further, the oil outlet end of the low pressure pump 8 is provided with an oil filter 17 for filtering the hydraulic oil.
Specifically, the execution unit comprises a first hydraulic cylinder assembly and a second hydraulic cylinder assembly, the first hydraulic cylinder assembly and the second hydraulic cylinder assembly respectively control the working state through an electro-hydraulic directional valve 34, and an oil inlet of the electro-hydraulic directional valve 34 is communicated with the main oil supply path 31. The electro-hydraulic directional valve is a hydraulic directional valve which is combined with an electromagnetic pilot valve into a whole. The electro-hydraulic directional valve 34 is a valve core pushed by pressure oil in a control oil path. The electro-hydraulic directional valve 34 is used to shift the direction of fluid flow.
Wherein, first hydraulic cylinder subassembly includes first pneumatic cylinder 37, is provided with the first steady voltage oil circuit that is used for the steady voltage between the oil inlet way of first pneumatic cylinder 37 and the oil outlet way. First steady voltage oil circuit is including connecting first branch road and the second branch road between the oil inlet way of first pneumatic cylinder 37 and the oil outlet way, be provided with the third check valve that two symmetries set up on the first branch road, be provided with the overflow valve 36 that two symmetries set up on the second branch road, first steady voltage oil circuit still includes pilot operated check valve 35, pilot operated check valve 35 third check valve and the cooperation of overflow valve 36 are used and are formed the steady voltage, and this is the steady voltage oil circuit commonly used among the prior art, and its specific setting is no longer repeated.
The second hydraulic cylinder assembly comprises a second hydraulic cylinder 38, and a second pressure stabilizing oil path for stabilizing pressure is also arranged between the oil inlet path and the oil outlet path of the second hydraulic cylinder 38. The second pressure stabilizing oil path has the same structure as the first pressure stabilizing oil path, and is not described herein again. Through setting up first steady voltage oil circuit and second steady voltage oil circuit for the oil pressure of the hydraulic oil of the oil feed end of first pneumatic cylinder 37 and second pneumatic cylinder 38 and the end that produces oil is stable during operation, and the shake when having avoided the operation of external operation spare part has improved the stability of hydraulic system operation.
In one embodiment, the first hydraulic cylinder 37 has a telescopic end connected to the push plate of the skip, and the second hydraulic cylinder 38 has a telescopic end connected to the hopper of the skip. In other embodiments, the telescoping ends of first and second cylinders 37, 38 are connected to the respective work members.
The first control valve comprises a proportional throttle valve 18 and a first one-way valve 19 which are sequentially arranged, the first one-way valve 19 is arranged close to the main oil supply path 31, and the proportional throttle valve 18 is arranged close to an oil outlet of the high-pressure pump 13 or the low-pressure pump 8. The proportional throttle valve 18 proportionally controls the hydraulic oil that enters the first check valve 19, and the hydraulic oil enters the main oil supply passage 31 through the first check valve 19. By providing the first check valve 19, the backflow of the hydraulic oil in the main oil supply passage 31 is prevented during operation.
In order to conveniently detect the oil pressure of the corresponding communicated oil path, a first pressure gauge 16 is arranged on the oil path close to the oil outlet end of the low-pressure pump 8 and/or the high-pressure pump 13, and the first pressure gauge 16 is communicated with the corresponding oil path sequentially through a pressure measuring hose 15 and a pressure measuring joint 14. A self-sealing valve is arranged in the pressure measuring joint 14, and when the pressure measuring joint is used alone, the self-sealing valve is closed under the action of a spring; after the self-sealing valve is butted with a measuring hose or a measuring joint with a thimble, the self-sealing valve can be opened for sampling of a high-pressure or low-pressure fluid system and system pressure detection. The pressure measuring hose 15 is connected with a pressure measuring joint 14, and a first pressure gauge 16 is conveniently connected to a hydraulic system.
The execution unit in the above embodiments includes a first hydraulic cylinder assembly and a second hydraulic cylinder assembly, and in other embodiments, the execution unit may also include one or more hydraulic cylinder assemblies, which is not limited herein.
In another specific embodiment, the execution unit further comprises a motor assembly, the motor assembly controls the working state through a proportional reversing valve 32, and an oil inlet of the proportional reversing valve 32 is communicated with the main oil supply path 31. In one embodiment, the motor assembly includes two motors 39 arranged in parallel, and the proportional directional valve 32 varies the size of the valve opening according to the magnitude of the given current or voltage, thereby controlling the speed of rotation of the motors 39. The proportional directional valve 32 controls the opening degree of the spool by a proportional solenoid. In one embodiment, the power output of the motor 39 drives the rail wheels of the skip car to rotate. In other embodiments, the output of the motor 39 may drive other rotationally operated components.
In another specific embodiment, the execution unit further comprises a buffer cylinder assembly, the buffer cylinder assembly controls the working state through the electromagnetic directional valve 28, and the oil inlet of the electromagnetic directional valve 28 is communicated with the main oil supply path 31. The cushion cylinder assembly includes two cushion cylinders 40 arranged in parallel. By providing the electromagnetic directional valve 28, the hydraulic oil entering the cushion cylinder 40 is controlled. In order to prevent the high-pressure hydraulic oil from flowing back during the operation of the cushion cylinder 40, a second check valve 33 is provided on the oil path near the oil inlet of the electromagnetic directional valve 28.
Further, in order to buffer vibration and reduce noise, the motor 10 is connected to the motor connecting seat through a motor damping bar 11.
In one embodiment, the inlet line of the cushion cylinder 40 is in communication with an accumulator 27. When power is cut off, the energy accumulator 27 provides hydraulic oil with set pressure for the buffer cylinder 40, so that the buffer cylinder 40 is guaranteed to stay at the working position at the moment of power cut, the working position change caused by pressure reduction in the buffer cylinder 40 is avoided, and the safety performance is improved. The energy accumulator 27 is also communicated with the oil tank 1 through a second oil return path, a second electromagnetic overflow valve 29 is arranged on the oil return path of the energy accumulator 27, and when the pressure in the energy accumulator 27 exceeds a set pressure range value, the second electromagnetic overflow valve 29 is opened to release the pressure until the pressure in the energy accumulator 27 is reduced to the set pressure range. The open end of the accumulator 27 is also provided with a safety ball valve 26 for extreme overload protection of the accumulator 27. The oil return passage of the motor assembly is communicated with the second oil return passage, a second oil return filter 23 is arranged on the second oil return passage at a position close to the oil tank 1, and a second air cooler 22 for cooling is arranged at an inlet position of the second oil return filter 23. Further, a second pressure gauge 30 for detecting oil pressure is provided at the outlet end of the accumulator 27. The connection mode and the connection structure between the second pressure gauge 30 refer to the first pressure gauge 16, and are not described herein.
Specifically, the oil outlet ends of the high-pressure pump 13 and the low-pressure pump 8 are both communicated with the oil tank 1 through a first oil return path, and a first oil return oil filter 25 is arranged on the first oil return path. The oil inlet ends of the high-pressure pump 13 and the low-pressure pump 8 are communicated with the oil tank 1 through oil inlet oil paths, and second control valves are arranged on the oil inlet oil paths. The second control valve comprises a ball valve 6, a compensation connecting pipe 7 is further arranged on the oil inlet circuit, and the compensation connecting pipe 7 is used for responding to length change of the oil inlet circuit along with temperature or stress.
In order to guarantee the normal work of high-pressure pump 13 and low-pressure pump 8, the utility model discloses a two hydraulic system that press still includes first air cooler 24, and first air cooler 24 is used for blowing the cooling to high-pressure pump 13 and low-pressure pump 8.
Wherein, still be provided with electric contact thermometer 2, liquid level relay 3, empty filter 4 and level gauge 5 on the oil tank 1, its mounting method is the same with the commonly used mounting method in this field, and the effect is also unanimous, and the no longer repeated description here.
Pump pressure adjustment of the low-pressure pump 8: the first electromagnetic overflow valve 20 is adjusted to make the low pressure higher than the set low pressure use pressure value by 0.5MPa, and then the pump pressure of the low pressure pump 8 is reduced to the set low pressure use pressure value of the system.
Pump pressure adjustment of the high-pressure pump 13: the high-pressure pump 13 has 3 working states of pressure relief, low pressure and high pressure. Firstly, adjusting a multi-stage electromagnetic overflow valve 21 to enable the low pressure of the high-pressure pump 13 to be consistent with the set low-pressure use pressure value of the system; then, adjusting the high-pressure overflow of the high-pressure pump 13 to enable the pressure value to be higher than the set high-pressure use pressure value of the system by 1.0 MPa; and finally, reducing the pressure of the high-pressure pump 13 to the set high-pressure use pressure value of the system.
In operation, the starter motor 10, the low-pressure pump 8 and the high-pressure pump 13 are started simultaneously, and the unloading electromagnet DT14 (second electromagnetic spill valve 29) of the accumulator 27 is always energized. A buffer lifting handle on the operation panel is powered on simultaneously by 2BDT, DT3 and DT12, and a buffer oil cylinder is lifted to the place; when the buffer descending handle is operated, the 2BDT, the DT2 and the DT13 are simultaneously electrified, and the buffer oil cylinder descends to the right position. When the motor works, DT1, DT3, DT13, 1BDT and 2BDT are electrified simultaneously, and the motor drives the left row (3BDT electrified) or the right row (4BDT electrified). A first oil cylinder handle on the operation panel, wherein 1BDT, 2BDT, DT1, DT2, DT13, DT8 and DT11 are electrified simultaneously, and the first hydraulic cylinder 37 advances to be at a low pressure; the second oil cylinder handle is operated, the 1BDT, the 2BDT, the DT1, the DT2, the DT13, the DT4 and the DT7 are simultaneously electrified, and the second oil cylinder 38 moves forwards and is in low pressure; the first hydraulic cylinder 37 and the second hydraulic cylinder 38 retract, the high pressure operates simultaneously, 2BDT, DT3, DT13, DT9 and DT10, and DT5 and DT6 are powered simultaneously. The above DT and BDT represent electromagnets corresponding to control valves, and for convenience of viewing, each electromagnet in fig. 1 is labeled, and is specifically referred to in the specification and fig. 1.
All the valves and the electric control part are in communication connection with the PLC, and are controlled by the PLC, and the connection and control method are common in the field and are not described again.
In the description of the present solution, it is to be understood that the terms "upper", "lower", "vertical", "inside", "outside", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus should not be construed as limiting the present solution.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present application, "a plurality" means two or more unless specifically limited otherwise.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other. The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (10)
1. The double-pressure hydraulic system is characterized by comprising a high-pressure pump and a low-pressure pump, wherein the high-pressure pump and the low-pressure pump are coaxially driven by a motor, the high-pressure pump and the low-pressure pump are communicated with an execution unit through a main oil supply way, and first control valves are arranged on the main oil supply way and communication oil ways between the high-pressure pump and the low-pressure pump; the oil outlet of the high-pressure pump is provided with a multi-stage electromagnetic overflow valve, and the oil outlet of the low-pressure pump is provided with a first electromagnetic overflow valve.
2. The dual-pressure hydraulic system of claim 1, wherein the actuation unit comprises a first hydraulic cylinder assembly and a second hydraulic cylinder assembly, the first and second hydraulic cylinder assemblies each controlling an operating state via an electro-hydraulic directional valve, an oil inlet of the electro-hydraulic directional valve being in communication with the main oil supply path.
3. The dual pressure hydraulic system of claim 1, wherein the first control valve comprises a proportional throttle valve and a first check valve arranged in series, the first check valve being disposed proximate the main oil supply.
4. The dual-pressure hydraulic system according to claim 1, wherein a first pressure gauge is provided on an oil path near an oil outlet end of the high-pressure pump and/or the low-pressure pump, and the first pressure gauge is used for detecting oil pressure of a corresponding communicating oil path.
5. The dual-pressure hydraulic system according to claim 4, wherein the first pressure gauge is in communication with the oil outlet of the high-pressure pump or the low-pressure pump through a pressure measuring hose, and the pressure measuring hose is in communication with the corresponding oil passage through a pressure measuring joint.
6. The dual pressure hydraulic system of claim 2, wherein the implement unit further comprises a motor assembly, the motor assembly controlling an operating state via a proportional directional valve, an oil inlet of the proportional directional valve being in communication with the main oil supply path.
7. The dual-pressure hydraulic system according to claim 2, wherein the execution unit further comprises a buffer cylinder assembly, the buffer cylinder assembly controls the working state through an electromagnetic directional valve, and an oil inlet of the electromagnetic directional valve is communicated with the main oil supply path; and a second one-way valve is arranged on an oil way close to the oil inlet of the electromagnetic directional valve.
8. The dual pressure hydraulic system of claim 7, wherein the dashpot assembly includes a dashpot having an oil inlet line in communication with an accumulator.
9. The dual pressure hydraulic system of claim 1, wherein the oil outlet ends of the high and low pressure pumps are each in communication with an oil tank through a first oil return line, the first oil return line having a first oil return filter disposed thereon; the oil inlet ends of the high-pressure pump and the low-pressure pump are communicated with the oil tank through oil inlet oil paths, and second control valves are arranged on the oil inlet oil paths.
10. The dual pressure hydraulic system of claim 1, further comprising a first air cooler for cooling the high pressure pump and the low pressure pump.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020830861.3U CN212455016U (en) | 2020-05-18 | 2020-05-18 | Double-pressure hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020830861.3U CN212455016U (en) | 2020-05-18 | 2020-05-18 | Double-pressure hydraulic system |
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| CN212455016U true CN212455016U (en) | 2021-02-02 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202020830861.3U Active CN212455016U (en) | 2020-05-18 | 2020-05-18 | Double-pressure hydraulic system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN118529131A (en) * | 2024-07-26 | 2024-08-23 | 江苏常矿工程机械有限公司 | Integrated hydraulic system of unmanned pure electric mining dump truck |
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2020
- 2020-05-18 CN CN202020830861.3U patent/CN212455016U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN118529131A (en) * | 2024-07-26 | 2024-08-23 | 江苏常矿工程机械有限公司 | Integrated hydraulic system of unmanned pure electric mining dump truck |
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