Novel ultrahigh pressure proportional valve and hydraulic control system

Abstract

According to the novel ultrahigh pressure proportional valve and the hydraulic control system, a piston cavity is formed in a valve body, a low-pressure piston block is arranged in the piston cavity, and a high-pressure cavity is formed in one side of the low-pressure piston block; the cavity body section of the high-pressure cavity is smaller than that of the piston cavity; a high-pressure piston block is arranged in the high-pressure cavity and is linked with the low-pressure piston block; the high-pressure cavity is connected with the high-pressure oil port, the piston cavity is connected with the low-pressure oil port, and one or more pressure relief oil ports are formed in the high-pressure cavity or the piston cavity. When the structure is used in a hydraulic control system, oil in the high-pressure cavity can be restrained to be discharged slowly through the low-pressure piston block, and the high-pressure cylinder can be controlled to stabilize pressure in a certain high-pressure state through proportional oil discharge. According to the hydraulic system, the defects in the prior art are overcome, stable control over the high-pressure oil cylinder can be achieved, during high-pressure unloading, the high pressure cannot be directly reduced to the lowest state, and linear unloading and pressure stabilization can be achieved.

Description

Technical Field

[0001] The utility model belongs to the technical field of hydraulic control systems, and particularly relates to a new type of ultra-high pressure proportional valve and a hydraulic control system. Background Art

[0002] As is well known, in the existing high-pressure pump station oil supply system, in its working state, by controlling the operation of the main pump, high-pressure oil is controlled to enter the main control system through a high-pressure single-phase valve. If such a high-pressure oil supply system is between 60 and 100 MPA, when the oil cylinder is depressurized, the oil returns through a reversing valve, and the high-pressure pump station oil supply system will directly drop from high pressure to low pressure, and the system will have no intermediate hydraulic load-bearing capacity inside.

[0003] Aiming at this drawback, the current urgent technical problem to be solved is to design a liquid-controlled proportional unloading valve for controlling the oil supply of the high-pressure pump station oil supply system. Through this liquid-controlled proportional unloading valve, the unloading state can be controlled orderly when the high-pressure oil cylinder is unloaded, and linear pressure supply within the high-pressure stage can be realized, avoiding the occurrence of the instantaneous pressure relief state from high to low of the high-pressure oil supply system. Summary of the Utility Model

[0004] In view of the above-mentioned disadvantages of the prior art pointed out, the utility model provides a new type of ultra-high pressure proportional valve and a hydraulic control system. By designing an ultra-high pressure proportional valve, controlling the high-pressure end at the low-pressure end through this proportional valve can not only control the pressure-holding state of the high-pressure oil cylinder, but also realize linear control of the staged pressure reduction or pressure stabilization of the high-pressure oil cylinder.

[0005] The technical solution adopted by the utility model to solve its technical problems is as follows:

[0006] A new type of ultra-high pressure proportional valve, which includes a valve body. A piston cavity is arranged inside the valve body. A low-pressure piston block is arranged inside the piston cavity, and a high-pressure cavity is arranged on one side of the low-pressure piston block; the cross-sectional area of the cavity of the high-pressure cavity is smaller than that of the piston cavity, and a high-pressure piston block is arranged inside the high-pressure cavity, or the high-pressure piston block is linked with the low-pressure piston block;

[0007] The high-pressure cavity is connected to a high-pressure oil port, the piston cavity is connected to a low-pressure oil port, and one or several pressure relief oil ports are arranged inside the high-pressure cavity or the piston cavity.

[0008] The low-pressure piston block and the high-pressure piston block are integrally structured, and the pressure relief oil port is arranged inside the high-pressure cavity; an elastic reset component is arranged inside the piston cavity to cooperate with the low-pressure piston block.

[0009] The described low-pressure piston block is provided with a groove, and the high-pressure elastic member is fixed through the groove. The high-pressure piston block is arranged in a taper structure and fixed on the high-pressure elastic member. A sealing area is arranged in the high-pressure cavity for cooperating with the high-pressure piston block, and the pressure relief oil port is arranged in the piston cavity.

[0010] A hydraulic control system includes an oil tank. A high-pressure pump and a low-pressure pump are arranged in the oil tank. The high-pressure pump is used to supply oil to the high-pressure cylinder, and a high-pressure overflow valve is arranged on the high-pressure oil supply pipeline. The low-pressure pump is used to supply oil to the low-pressure cylinder, and a low-pressure overflow valve is arranged on the low-pressure oil supply pipeline.

[0011] The described new type of ultra-high pressure proportional valve is arranged between the oil discharge pipeline of the high-pressure oil cylinder and the low-pressure pump.

[0012] A manual reversing valve is connected to the high-pressure oil cylinder and is connected to the new type of ultra-high pressure proportional valve through the manual reversing valve.

[0013] A low-pressure unloading proportional valve is connected to the low-pressure cylinder.

[0014] The utility model has the following beneficial effects: The utility model discloses a new type of ultra-high pressure proportional valve, which is provided with a piston cavity in the valve body. A low-pressure piston block is arranged in the piston cavity, and a high-pressure cavity is arranged on one side of the low-pressure piston block. The cross-sectional area of the high-pressure cavity is smaller than that of the piston cavity. A high-pressure piston block is arranged in the high-pressure cavity, and the high-pressure piston block is linked with the low-pressure piston block. The high-pressure cavity is connected to the high-pressure oil port, and the piston cavity is connected to the low-pressure oil port. One or several pressure relief oil ports are arranged in the high-pressure cavity or the piston cavity. When the above structure is used in a hydraulic control system, the oil in the high-pressure cavity can be restricted by the low-pressure piston block to slowly discharge, and the high-pressure oil cylinder can be stabilized at a certain high-pressure state through proportional oil discharge control.

[0015] The utility model overcomes the drawbacks in the prior art, can realize the stable control of the high-pressure oil cylinder, and when the high-pressure is unloaded, it will not directly drop from the high pressure to the lowest state, and can realize linear unloading. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The following further describes the utility model with reference to the drawings and embodiments.

[0017] Figure 1 It is a schematic structural diagram of the new type of ultra-high pressure proportional valve;

[0018] Figure 2 It is a schematic diagram of the use state of the new type of ultra-high pressure proportional valve Figure Ⅰ ;

[0019] Figure 3 It is a schematic diagram of the use state of the new type of ultra-high pressure proportional valve Figure Ⅱ ;

[0020] In the figure:

[0021] 1. Fuel tank, 11. Air filter;

[0022] 2. Motor;

[0023] 3. New type ultra-high pressure proportional valve, 30. Valve body, 31. Low-pressure oil port, 32. High-pressure oil port, 33. High-pressure cavity, 34. Plugging area, 35. Pressure relief oil port, 36. High-pressure tapered piston block, 361. High-pressure spring, 37. Low-pressure piston block, 371. Low-pressure sealing ring, 372. High-pressure columnar piston block, 373. Low-pressure upper spring, 374. High-pressure sealing ring, 38. Low-pressure cavity, 381. Low-pressure lower spring;

[0024] 4. High-pressure oil supply system, 41. High-pressure pump, 42. High-pressure check valve, 43. High-pressure relief valve;

[0025] 5. Low-pressure oil supply system, 51. Low-pressure pump, 52. Low-pressure check valve, 53. Low-pressure relief valve;

[0026] 6. Manual reversing valve;

[0027] 7. High-pressure oil cylinder, 71. Liquid supply check valve;

[0028] 8. Low-pressure unloading proportional valve. Detailed implementation mode

[0029] The present utility model will be further described through the implementation mode below. The following description is only for exemplary explanation. Those skilled in the art can make further structural improvements based on the following explanation. The protection scope of this patent shall be subject to the scope recorded in the claims.

[0030] Embodiment 1:

[0031] A new type ultra-high pressure proportional valve 3, as shown in the appendix Figure 2 shown, which includes a valve body 30. A piston cavity is arranged in the valve body 30. A low-pressure piston block 37 is arranged in the piston cavity. A low-pressure sealing ring 371 is arranged around the low-pressure piston block 37. The radial seal during the movement of the low-pressure piston block 37 is realized through the low-pressure sealing ring 371.

[0032] The low-pressure piston block 37 divides the cavity in the piston cavity. The lower part of the low-pressure piston block 37 is a low-pressure cavity 38; a high-pressure cavity 33 is arranged on the upper side of the low-pressure piston block 37; it should be noted that the cross-sectional area of the cavity of the high-pressure cavity 33 is smaller than that of the piston cavity, that is, the low-pressure cavity 38. The difference ratio of such cross-sectional areas can be calculated proportionally under the guidance of the specification. Those skilled in the art can calculate according to the specific requirements of the proportional valve, and this proportional calculation is the same as the numerical calculation method of the proportional valve in the prior art, and no detailed description will be given here.

[0033] A high-pressure columnar piston block 372 is arranged in the high-pressure cavity 33, and a high-pressure sealing ring 374 is arranged around the high-pressure columnar piston block 372. The radial seal during the movement of the high-pressure columnar piston block 372 is realized through the high-pressure sealing ring 374. The low-pressure piston block 37 and the high-pressure columnar piston block 372 are integrally structured, and this structure can realize the linkage between the high-pressure columnar piston block 372 and the low-pressure piston block 37.

[0034] The high-pressure cavity 33 is connected to the high-pressure oil port 32, and the piston cavity (low-pressure cavity 38) is connected to the low-pressure oil port 31. In the piston cavity, two pressure relief oil ports 35 are arranged above the low-pressure piston block 37. In the low-pressure cavity 38, a low-pressure upper spring 373 and a low-pressure lower spring 383 are respectively arranged above and below the low-pressure piston block 37 and are used in cooperation with the low-pressure piston block 37 as elastic reset components.

[0035] With the above structural arrangement, in actual application, taking the working system of a high-pressure oil cylinder with a pressure of 60 - 100 MPA as an example for explanation, after the high-pressure oil port 32 is set at a constant pressure of 60 - 100 MPA, high-pressure oil enters the high-pressure cavity 33, pushing the low-pressure piston block 37 below the pressure relief oil port 35 to achieve high-pressure oil unloading. At this time, low-pressure oil (with adjustable pressure) is added to the low-pressure cavity 38, and the low-pressure piston block 37 moves upward. According to the pressure regulating piston ratio, the low-pressure piston block 37 moves upward, promoting the slow unloading of the oil in the high-pressure cavity 33. The oil pressure in the high-pressure cavity 33 starts to increase, and according to the ratio of the high-pressure cavity 33 to the low-pressure cavity 38 on the low-pressure piston block 37, the oil in the high-pressure cavity rises to 60 - 100 MPA, thereby realizing that the high-pressure oil cylinder can achieve linear pressure regulation and staged voltage stabilization.

[0036] Embodiment 2:

[0037] Based on Embodiment 1, a new type of ultra-high pressure proportional valve 3, as shown in the appendix Figure 3 shows, which includes a valve body 30. A piston cavity is arranged in the valve body 30, and a low-pressure piston block 37 is arranged in the piston cavity. A low-pressure sealing ring 371 is arranged around the low-pressure piston block 37. The radial seal during the movement of the low-pressure piston block 37 is realized through the low-pressure sealing ring 371.

[0038] The low-pressure piston block 37 divides the cavity in the piston cavity. The lower part of the low-pressure piston block 37 is the low-pressure cavity 38. A high-pressure cavity 33 is arranged above the low-pressure piston block 37. It should be noted that the cross-sectional area of the cavity of the high-pressure cavity 33 is smaller than that of the piston cavity, that is, the low-pressure cavity 38. The difference ratio of this cross-sectional area can be calculated proportionally under the guidance of the specification. Those skilled in the art can calculate according to the specific requirements of the proportional valve, and this proportional calculation is the same as the numerical calculation method of the proportional valve in the prior art, and no detailed description will be given here.

[0039] A sealing area 34 is provided at the interface between the high-pressure chamber 33 and the piston chamber. A high-pressure tapered piston block 36 is provided in cooperation with the sealing area 34. A high-pressure spring 361 is provided at the lower part of the high-pressure tapered piston block 36. A groove is provided on the low-pressure piston block 37, and the high-pressure spring 361 is fixed through the groove. The sealing area 34 is provided in the high-pressure chamber 33 for cooperation with the high-pressure tapered piston block 36. The pressure relief oil port 35 is provided in the piston chamber.

[0040] Through the above structural arrangement, the oil inlet volume of the low-pressure oil port 31 can be controlled to drive the low-pressure piston block 37 in the low-pressure chamber 38 to move upward. At this time, the high-pressure oil port 32 connects the high-pressure chamber 33 and the external high-pressure oil cylinder 7. When the high-pressure end is unloaded, the high-pressure oil port 32 pushes the high-pressure tapered piston block 36 downward, and the downward movement speed and the downward movement amount of the high-pressure tapered piston block 36 can be controlled by the oil inlet volume of the low-pressure oil port 31. In actual application, taking the working system of a high-pressure oil cylinder with a pressure of 60 - 100 MPA as an example for explanation, high-pressure oil at a rated pressure of 60 - 100 MPA enters the high-pressure chamber 33 through the high-pressure oil port 32, pushing the high-pressure tapered piston block 36 below the pressure relief oil port 35, and the high-pressure oil is unloaded, and the high-pressure chamber has no pressure. At this time, low-pressure oil pressure (the pressure is adjustable) is added to the low-pressure chamber 38, and the low-pressure chamber 38 is slowly pressurized, and the high-pressure tapered piston block 36 slowly moves upward. Since the diameter of the low-pressure piston block 37 is more than 3 times that of the high-pressure tapered piston block 36, at this time, the low-pressure piston block 37 pushes the high-pressure spring 361 and the high-pressure tapered piston block 36 upward, so that the high-pressure oil in the high-pressure chamber cannot return oil quickly, thereby realizing that the high-pressure oil cylinder can achieve linear pressure regulation and staged pressure stabilization.

[0041] Embodiment 3:

[0042] The present utility model realizes the application of a new type of ultra-high pressure proportional valve based on a hydraulic control system. As Figure 1 shown, a hydraulic control system includes an oil tank 1, and an air filter 11 is provided in the oil tank 1.

[0043] An electric motor 2 is further provided in the oil tank 1 to drive the operation of a high-pressure oil supply system 4 and a low-pressure oil supply system 5. The high-pressure oil supply system 4 includes a high-pressure pump 41 and a high-pressure one-way valve 42; the low-pressure oil supply system 5 includes a low-pressure pump 51 and a low-pressure one-way valve 52; after the above structural arrangement, the high-pressure oil supply system 4 supplies oil to the high-pressure oil cylinder 7, and the low-pressure oil supply system 5 supplies oil to the new type of ultra-high pressure proportional valve 3. In this embodiment, the new type of ultra-high pressure proportional valve 3 is arranged between the oil discharge pipeline of the high-pressure oil cylinder 7 and the low-pressure pump 51.

[0044] The utility model is provided with a high-pressure overflow valve 43, a manual reversing valve 6, and a liquid supply check valve 7 on the high-pressure oil supply pipeline; the low-pressure pump 51 is used to supply oil to the low-pressure chamber 38 in the new type of ultra-high pressure proportional valve 3. The purposes of the above-mentioned high-pressure oil supply and low-pressure oil supply are to realize the movement of the low-pressure piston block 37 in Embodiment 1 and Embodiment 2, and at the same time realize the pressurization effect of the high-pressure oil cylinder 7.

[0045] The utility model is also provided with a low-pressure overflow valve 53 on the low-pressure oil supply pipeline. During actual operation, it is necessary to ensure that there is no instantaneous pressure loss in the new type of ultra-high pressure proportional valve 3. Therefore, a low-pressure unloading proportional valve 8 is connected to the low-pressure chamber 38 to simultaneously realize the linear control of the new type of ultra-high pressure proportional valve 3.

Claims

1. A new type of ultra-high pressure proportional valve, characterized by: It comprises a valve body, a piston cavity is arranged in the valve body, a low-pressure piston block is arranged in the piston cavity, and a high-pressure cavity is arranged on one side of the low-pressure piston block; the cavity cross section of the high-pressure cavity is smaller than the cavity cross section of the piston cavity, a high-pressure piston block is arranged in the high-pressure cavity, or the high-pressure piston block and the low-pressure piston block are linked; The high-pressure chamber is connected to the high-pressure oil port, the piston chamber is connected to the low-pressure oil port, and a single or multiple pressure relief oil ports are arranged in the high-pressure chamber or the piston chamber.

2. A novel ultra-high pressure proportional valve as claimed in claim 1, characterized in that: The low-pressure piston block and the high-pressure piston block are arranged as an integrated structure, and the pressure relief oil port is arranged in the high-pressure chamber; an elastic reset component is arranged in the piston chamber to cooperate with the low-pressure piston block.

3. A novel ultra-high pressure proportional valve as claimed in claim 1, characterized in that: The low-pressure piston block is provided with a groove, through which the high-pressure elastic part is fixed. The high-pressure piston block is provided with a tapered structure and is fixed on the high-pressure elastic part. A sealing area is provided in the high-pressure cavity for use in conjunction with the high-pressure piston block. The pressure relief oil port is provided in the piston cavity.

4. A hydraulic control system, which adopts any one of the new ultra-high pressure proportional valves of claims 1-3, characterized in that: It includes an oil tank, in which a high-pressure pump and a low-pressure pump are arranged. The high-pressure pump is used to supply oil to the high-pressure cylinder and a high-pressure relief valve is arranged on the high-pressure oil supply pipeline; the low-pressure pump is used to supply oil to the low-pressure cylinder and a low-pressure relief valve is arranged on the low-pressure oil supply pipeline; The novel ultra-high pressure proportional valve is arranged between the oil unloading pipeline of the high pressure oil cylinder and the low pressure pump.

5. A hydraulic control system according to claim 4, characterized in that: The high-pressure oil cylinder is connected with a manual reversing valve.

6. A hydraulic control system according to claim 4, characterized in that: The low-pressure cylinder is connected with a low-pressure unloading proportional valve.

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