Oil inlet and outlet structure for supercharging device and booster pump thereof

Abstract

The invention discloses an oil inlet and outlet structure for a supercharging device and a booster pump thereof, and belongs to the field of supercharging devices. The oil inlet and outlet structure further comprises a second oil inlet passage or a second oil outlet passage located between an end cover and a reversing valve body; wherein one end of the first oil inlet passage is connected with a first cavity separated by a piston of the supercharging device, and the other end is connected with external hydraulic oil of the supercharging device; one end of the first oil outlet passage is connected with a second cavity separated by a piston of the supercharging device, and the other end is connected with external hydraulic oil of the supercharging device; one end of the second oil inlet passage is connected with the second cavity, and the other end is connected with external hydraulic oil of the supercharging device; one end of the second oil outlet passage is connected with the first cavity, and the other end is connected with external hydraulic oil. Oil storage is provided through the second oil inlet channel or the second oil outlet channel located between the end cover and the reversing valve body, and oil inlet / outlet oil path buffering generated when the piston of the supercharging device moves in the second direction is provided for hydraulic oil in the first cavity or the second cavity.

Description

Technical Field

[0001] This invention relates to the field of booster technology, and in particular to an oil inlet / outlet structure for a booster and its booster pump. Background Technology

[0002] The air-driven liquid booster pump is a positive displacement booster device that uses compressed air (0.1–0.8 MPa) as a power source and boosts low-pressure liquids based on Pascal's principle. Its core structure consists of an air-driven section and a liquid-driven section. A large-diameter air-driven piston and a small-diameter liquid booster plunger are rigidly linked, with a sealed isolation structure to prevent air-liquid leakage. It is also equipped with auxiliary components such as an air-controlled directional valve and inlet / outlet check valves. The air-controlled directional valve automatically switches the direction of compressed air intake, driving the piston to reciprocate, which in turn drives the booster plunger to move synchronously, achieving a continuous cycle of "liquid suction—boosting—discharging." The pump's output pressure is determined by the driving air pressure and the booster ratio (the area ratio of the air-driven piston to the liquid-driven plunger), typically between 2:1 and 200:1. The maximum output pressure can reach 600 MPa, and it features an automatic pressure-holding function. When the output pressure reaches the set value, the pump automatically stops. If system leakage causes a pressure drop, it automatically replenishes the pressure. The pressure-holding process consumes no additional energy. Pneumatic liquid booster pumps can be classified into single-acting, double-acting, and multi-stage booster types according to their structure. Single-acting pumps have a simple structure but a small flow rate. Double-acting pumps can increase the output flow rate by alternating pressure at both ends. Multi-stage booster pumps can achieve cross-stage pressure boosting from low pressure to ultra-high pressure. They have strong media adaptability and can boost hydraulic oil, water, ethylene glycol, and some acid and alkali media. With the characteristics of non-electric drive, explosion-proof safety, compact structure, and convenient maintenance, they are widely used in high-pressure withstand testing, hydraulic clamp fastening, metal forming, and outdoor mobile hydraulic operations in explosion-proof scenarios such as chemical industry, oil and gas fields, and coal mines.

[0003] In existing technologies, double-acting pumps are often used to increase flow rate. The hydraulic circuit is designed with symmetrical double inlet and double outlet (one inlet and one outlet at each end). The inlet / outlet check valves are symmetrically arranged on both sides of the booster chamber along the axis of the booster cylinder. The medium is delivered directly in and out without buffering. Significant pressure fluctuations can easily occur when the pump body switches back and forth. The instantaneous peak and valley values ​​of the pressure will cause the pressure at the high-pressure output end to fluctuate, making it impossible to maintain a constant target pressure. This makes it difficult to meet the demanding requirements for pressure stability in high-precision pressure resistance testing, precision hydraulic forming, and other working conditions.

[0004] Therefore, a new oil inlet / outlet structure is urgently needed to solve the above-mentioned technical problems. Summary of the Invention

[0005] In order to overcome the shortcomings of the prior art, the purpose of the present invention is to provide oil storage through a second oil inlet passage or a second oil outlet passage located between the end cover and the reversing valve body, so as to provide oil circuit buffer for the hydraulic oil in the first chamber or the second chamber when the piston of the booster device moves in the second direction.

[0006] The objective of this invention is achieved through the following technical solution: An oil inlet / outlet structure for a booster unit includes a first oil inlet passage located on the booster unit end cover, a first oil outlet passage located on the booster unit reversing valve body, and a second oil inlet passage located between the end cover and the reversing valve body; wherein... The first oil inlet passage is connected at one end to the first chamber separated by the piston of the booster device, and at the other end to the external hydraulic oil of the booster device; The first oil outlet passage is connected at one end to the second chamber separated by the piston of the booster device, and at the other end to the external hydraulic oil of the booster device; The second oil inlet passage is connected at one end to the second chamber and at the other end to the external hydraulic oil of the booster device; When the piston of the booster moves in the first direction, external hydraulic oil enters the first chamber through the first oil inlet passage, and at this time the oil in the second chamber is discharged through the first oil outlet passage. When the booster piston moves in the second direction, which is opposite to the first direction, the external hydraulic oil enters the second chamber smoothly under the buffering effect of the second oil inlet passage, so as to reduce oil pressure fluctuations.

[0007] Preferably, it also includes an oil supply line located inside the end cover of the booster device, the oil supply line being connected to the first oil inlet passage and the second oil inlet passage respectively.

[0008] Preferably, the first oil inlet passage includes a first oil inlet valve, the first oil inlet valve includes a seal, a valve core and a return spring, the booster device end cover is provided with an oil inlet hole, the seal, the valve core and the return spring are located in the oil inlet hole in sequence, the return spring abuts against the valve core and the end of the oil inlet hole respectively, and the seal seals the gap between the valve core and the oil inlet hole.

[0009] Preferably, the valve core is a ball valve core.

[0010] Preferably, the second oil inlet pipe extends from the end cover of the booster device towards the reversing valve body of the booster device.

[0011] A booster pump includes the aforementioned oil inlet and outlet structures for the booster device.

[0012] An oil inlet and outlet structure for a booster unit includes a first oil inlet passage located on the booster unit end cover, a first oil outlet passage located on the booster unit reversing valve body, and a second oil outlet passage located between the end cover and the reversing valve body; wherein... The first oil inlet passage is connected at one end to the first chamber separated by the piston of the booster device, and at the other end to the external hydraulic oil of the booster device; The first oil outlet passage is connected at one end to the second chamber separated by the piston of the booster device, and at the other end to the external hydraulic oil of the booster device; The second oil outlet passage is connected at one end to the first chamber and at the other end to the external hydraulic oil of the booster device; When the piston of the booster moves in the first direction, external hydraulic oil enters the first chamber through the first oil inlet passage, and at this time the oil in the second chamber is discharged through the first oil outlet passage. When the piston of the booster device moves in the second direction, which is opposite to the first direction, the hydraulic oil in the first chamber is smoothly discharged through the second oil outlet passage under the buffering effect of the second oil outlet passage, so as to reduce oil pressure fluctuation.

[0013] Preferably, the second oil outlet passage includes a main oil outlet passage and a secondary oil outlet passage one and a secondary oil outlet passage two located in the end cover of the booster device and the reversing valve body of the booster device, respectively.

[0014] Preferably, the inner diameter of the main oil outlet passage is larger than the inner diameter of the secondary oil outlet passage.

[0015] A booster pump includes the aforementioned oil inlet and outlet structures for the booster device.

[0016] Compared with existing technologies, the oil inlet / outlet structure and booster pump of this invention for a booster device have the following advantages: (1) This application uses a second oil inlet passage located between the end cover and the reversing valve body. When moving in the second direction, the external hydraulic oil first passes through the second oil inlet passage and is pre-buried with pressure. When it enters the second chamber, the oil volume is stably input, which reduces the pressure fluctuation generated by the piston of the booster device switching back and forth.

[0017] (2) This application includes a booster pump with a second oil inlet passage, which can provide oil circuit buffer for the hydraulic oil in the second chamber when the piston of the booster device moves in the second direction, and is suitable for working conditions with strict requirements for pressure stability, such as high-precision pressure resistance testing and precision hydraulic forming.

[0018] (3) This application uses a second oil outlet passage located between the end cover and the reversing valve body. When moving in the second direction, the hydraulic oil located in the first chamber is pre-output to the second oil outlet passage and then discharged through the second oil outlet passage with stable oil volume, thereby reducing the pressure fluctuation generated by the piston of the booster device switching back and forth.

[0019] (4) This application includes a booster pump with a second oil outlet passage, which can provide oil circuit buffer for the hydraulic oil in the first chamber when the piston of the booster device moves in the second direction, and is suitable for working conditions with strict requirements for pressure stability, such as high-precision pressure resistance testing and precision hydraulic forming. Attached Figure Description

[0020] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and, together with their descriptions, serve to explain the invention and do not constitute an undue limitation of this application. In the drawings: Figure 1 This is a cross-sectional view of the first oil inlet passage of the present invention; Figure 2 This is a cross-sectional view of the first oil outlet passage of the present invention; Figure 3 This is a cross-sectional view of the structure of the second oil inlet passage of the present invention; Figure 4 This is a cross-sectional view of the end cover of the pressurization device of the present invention; Figure 5 This is a schematic diagram of the booster pump according to the second embodiment of the present invention; Figure 6 This is an exploded view of the booster pump according to the second embodiment of the present invention; Figure 7 This is a cross-sectional view of the reversing valve body and pressure block of the booster device of the present invention; Figure 8 This is a cross-sectional view of the structure of the second oil outlet passage of the present invention; Figure 9 This is a schematic diagram of the booster pump according to the fourth embodiment of the present invention; Figure 10 This is an exploded view of the booster pump according to the fourth embodiment of the present invention; Figure 11 This is a comparative schematic diagram of the pressure fluctuation curve A without a second oil inlet passage or a second oil outlet passage and the pressure fluctuation curve B with a second oil inlet passage or a second oil outlet passage.

[0021] In the diagram: 1000, booster pump; 10, end cap; 11, oil pipeline; 12, oil inlet port; 20, reversing valve body; 21, pneumatic reversing valve; 22, drive piston; 23, piston rod; 30, piston; 40, first chamber; 50, second chamber; 60, first oil inlet passage; 61, first oil inlet valve; 611, seal; 612, valve core; 613, return spring; 70, first oil outlet passage; 71, first oil outlet branch; 72, second oil outlet branch; 73, first oil outlet valve; 80, 80a, 80b, second oil inlet passage; 81, second oil inlet valve; 82, oil inlet branch; 90, 90a, 90b, second oil outlet passage; 91, main oil outlet passage; 92, secondary oil outlet passage one; 93, secondary oil outlet passage two; 94, second oil outlet valve; 100, pressure block. Detailed Implementation

[0022] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0023] It should be noted that when a component is said to be "fixed to" another component, it can be directly on the other component or it can be fixed through another intermediate component. When a component is said to be "connected to" another component, it can be directly connected to the other component or it may be fixed through another intermediate component. When a component is said to be "set on" another component, it can be set directly on the other component or it may be set through another intermediate component. The terms "vertical," "horizontal," "left," "right," and similar expressions used in this document are for illustrative purposes only.

[0024] Example 1: Figures 1-4 This invention provides an oil inlet / outlet structure for a booster device, such as... Figure 1 , Figure 2 As shown, it includes a first oil inlet passage 60 located on the end cover 10 of the booster device and a first oil outlet passage 70 located on the reversing valve body 20 of the booster device. The booster device piston 30 is located in the cavity between the end cover 10 and the reversing valve body 20, and the piston 30 divides the cavity into a first chamber 40 and then a second chamber 50.

[0025] like Figure 3 As shown, the oil inlet and outlet structure for the booster device also includes a second oil inlet passage 80, 80a, 80b located between the end cover 10 and the reversing valve body 20.

[0026] Specifically, the second oil inlet passages 80, 80a, and 80b extend from the end cover 10 of the booster unit towards the reversing valve body 20 of the booster unit.

[0027] The diameters of the second oil inlet passages 80, 80a, and 80b are larger than the diameter of the first oil outlet passage 70.

[0028] The longitudinal lengths of the second oil inlet passages 80, 80a, and 80b are greater than the longitudinal length of the second chamber 50.

[0029] The first oil inlet passage 60 is connected at one end to the first chamber 40 separated by the piston 30 of the booster device, and at the other end to the external hydraulic oil of the booster device; the first oil outlet passage 70 is connected at one end to the second chamber 50 separated by the piston 30 of the booster device, and at the other end to the external hydraulic oil of the booster device; the second oil inlet passages 80, 80a, and 80b are connected at one end to the second chamber 50, and at the other end to the external hydraulic oil of the booster device.

[0030] The second oil outlet passage 90A is located inside the end cover 10, and the hydraulic oil in the first chamber 40 is connected to the external hydraulic oil of the booster device through the second oil outlet passage 90A.

[0031] When the piston 30 of the booster device moves in the first direction, external hydraulic oil enters the first chamber 40 through the first oil inlet passage 60, and at this time the oil in the second chamber 50 is discharged through the first oil outlet passage 70. When the piston 30 of the booster device moves in the second direction, which is opposite to the first direction, the external hydraulic oil enters the second chamber 50 smoothly under the buffering effect of the second oil inlet passages 80, 80a, and 80b, so as to reduce oil pressure fluctuations.

[0032] Specifically, the first direction is from the end cover 10 of the booster device to the reversing valve body 20 of the booster device; the second direction is from the reversing valve body 20 of the booster device to the end cover 10 of the booster device.

[0033] Specifically, such as Figure 4 As shown, it also includes an oil supply line 11 located inside the end cover 10 of the booster device, and the oil supply line 11 is connected to the first oil inlet passage 60, the second oil inlet passages 80, 80a and 80b respectively.

[0034] Specifically, the first oil inlet passage 60 and the second oil inlet pipeline 80B are arranged in parallel.

[0035] Specifically, the first oil inlet passage 60 includes a first oil inlet valve 61, which includes a seal 611, a valve core 612, and a return spring 613. The booster device end cover 10 is provided with an oil inlet hole 12. The seal 611, the valve core 612, and the return spring 613 are located sequentially in the oil inlet hole 12. The return spring 613 abuts against the valve core 612 and the end of the oil inlet hole 12, respectively. The seal 611 seals the gap between the valve core 612 and the oil inlet hole 12.

[0036] In a preferred embodiment of this application, the valve core 612 is a ball valve core.

[0037] The first inlet valve 61 is a check valve. This application also includes a second inlet valve 81 with the same structure as the first inlet valve 61.

[0038] Specifically, the second oil inlet passages 80, 80a, and 80b also include an oil inlet branch 82. The axis of the oil inlet branch 82 is perpendicular to the axis of the second oil inlet passages 80, 80a, and 80b, and connects the second oil inlet passages 80, 80a, and 80b to the second chamber 50, respectively.

[0039] The first oil outlet passage 70 includes a first oil outlet branch 71, a second oil outlet branch 72, and a first oil outlet valve 73.

[0040] Specifically, such as Figure 2 , Figure 4 As shown, the first oil outlet branch 71 is connected to the second chamber 50, and the first oil outlet branch 71 and the second oil outlet branch 72 are connected in sequence and located in the reversing valve body 20. The first oil outlet valve 73 is connected to the second oil outlet branch 72. The pressure block 100 is fixed to one side of the reversing valve body 20. The pressure block 100 is provided with a pipeline connected to the first oil outlet passage 70 to connect to the outside.

[0041] Specifically, the inner diameter of the first oil outlet passage 70 is 0.5 mm.

[0042] Specifically, the axis of the first oil outlet branch 71 is perpendicular to the axis of the booster piston 30, and the first oil outlet branch 71 extends upward.

[0043] The implementation process is as follows: When the booster piston 30 moves in the first direction, external hydraulic oil enters the first chamber 40 through the first oil inlet passage 60. At this time, the oil in the second chamber 50 is discharged through the first oil outlet passage 70. When the booster piston 30 moves in the second direction, which is opposite to the first direction, the external hydraulic oil smoothly enters the second chamber 50 under the buffering effect of the second oil inlet passages 80, 80a, and 80b, thereby reducing oil pressure fluctuations. This application utilizes the second oil inlet passages 80, 80a, and 80b located between the end cover 10 and the reversing valve body 20. The second oil inlet passages 80, 80a, and 80b have a certain oil storage capacity, which can provide oil path buffering for the hydraulic oil in the second chamber 50 generated by the booster piston 30 moving in the second direction. This is suitable for high-precision pressure resistance testing, precision hydraulic molding, and other working conditions with stringent pressure stability requirements. This application utilizes second oil inlet passages 80, 80a, and 80b located between the end cover 10 and the reversing valve body 20. During movement in the second direction, external hydraulic oil first passes through the second oil inlet passages 80, 80a, and 80b, receiving pre-pressure buffering before entering the second chamber 50. For example... Figure 11 As shown, the pressure fluctuation curve B after setting the second oil inlet passages 80, 80a, and 80b shows that, compared to the pressure fluctuation curve A, the frequency of pressure fluctuations between 12MPa and 15MPa is significantly reduced. The pressure fluctuations between peaks and valleys are smoother per unit time, reducing the "intenseness" of the pressure fluctuations and making the fluctuations between peaks and valleys smoother. This achieves stable oil input, alleviates the pressure sudden change during piston 30 switching, and reduces the pressure fluctuations generated when piston 30 of the booster device switches back and forth.

[0044] Example 2: like Figures 1-6 As shown, this application is a booster pump 1000 including the oil inlet and outlet structure for the booster device in Embodiment 1 above.

[0045] Among them, such as Figure 5 As shown, the booster pump 1000 includes an end cover 10 and a reversing valve body 20. The reversing valve body 20 of this application includes a pneumatic reversing valve 21, a piston rod 23, and a drive piston 22 located on one side of the piston rod 23. The pneumatic reversing valve 21 automatically switches the intake direction of compressed air, drives the drive piston 22 to reciprocate, and then drives the booster device piston 30 to move synchronously, so as to realize the reciprocating cycle of oil suction and oil discharge.

[0046] The end cap 10 and the reversing valve body 20 are provided with a cavity, and a booster piston 30 is provided in the cavity. The booster piston 30 is coaxially arranged with the drive piston 22 and is located on the other side of the piston rod 23. The booster piston 30 divides the cavity into a first chamber 40 and a second chamber 50.

[0047] It also includes a first oil inlet passage 60 located on the end cover 10, a first oil outlet passage 70 located on the reversing valve body 20, and a second oil inlet passage 80, 80a, 80b located between the end cover 10 and the reversing valve body 20.

[0048] Among them, the second oil inlet passages 80, 80a, and 80b have larger diameters and a certain amount of oil storage capacity. When the pneumatic control reversing valve 21 automatically switches the intake of compressed air, it can reduce the obvious pressure fluctuations that may easily occur when the piston 30 of the booster device switches back and forth.

[0049] The implementation process is as follows: When the pneumatic reversing valve 21 drives the driving piston 22 to move in the first direction, it drives the booster piston 30 to move in the same direction. At this time, external hydraulic oil is input into the first chamber 40 through the first oil inlet passage 60, and the oil in the second chamber 50 is discharged through the first oil outlet passage 70. When the pneumatically controlled directional valve 21 drives the drive piston 22 to move in the second direction, it drives the booster piston 30 to move in the same direction. The second direction is opposite to the first direction. At this time, external hydraulic oil is input into the second chamber 50 through the second oil inlet passages 80, 80a, and 80b. The oil in the first chamber 40 is discharged through the second oil outlet passages 90, 90a, and 90b located in the end cover 10, thereby realizing the oil suction and discharge cycle of the booster pump 1000. Using this booster pump 1000, the oil inlet pressure fluctuation is small, such as... Figure 11 As shown, after setting the second oil inlet passages 80, 80a, and 80b, the pressure fluctuation between peaks and valleys per unit time is smoother, which can adapt to the demanding working conditions such as high-precision pressure resistance testing and precision hydraulic forming that require strict pressure stability.

[0050] Example 3: Figure 1 , Figure 2 , Figure 7 , Figure 8 This invention provides an oil inlet / outlet structure for a booster device, such as... Figure 1 , Figure 2 As shown, it includes a first oil inlet passage 60 located on the end cover 10 of the booster device and a first oil outlet passage 70 located on the reversing valve body 20 of the booster device. The booster device piston 30 is located in the cavity between the end cover 10 and the reversing valve body 20, and the piston 30 divides the cavity into a first chamber 40 and then a second chamber 50. It also includes a second oil outlet passage 90, 90a, and 90b located between the end cover 10 and the reversing valve body 20.

[0051] like Figure 2As shown, the first oil outlet branch 71 is connected to the second chamber 50, and the first oil outlet branch 71 and the second oil outlet branch 72 are connected in sequence and located in the reversing valve body 20. The first oil outlet valve 73 is connected to the second oil outlet branch 72. The pressure block 100 is fixed to one side of the reversing valve body 20. The pressure block 100 is provided with a pipeline connected to the first oil outlet passage 70 to connect to the outside.

[0052] Specifically, the second oil inlet passages 80, 80a, and 80b are located on the reversing valve body 20 and are connected to the second chamber 50.

[0053] Specifically, the second oil outlet passages 90, 90a, and 90b extend from the end cover 10 of the booster unit towards the reversing valve body 20 of the booster unit.

[0054] Specifically, the inner diameter of the first oil outlet passage 70 is 0.5 mm.

[0055] The diameters of the second oil outlet passages 90, 90a, and 90b are larger than the diameter of the first oil outlet passage 70.

[0056] The longitudinal lengths of the second oil outlet passages 90, 90a, and 90b are greater than the longitudinal length of the first chamber 40.

[0057] Specifically, such as Figure 7 , Figure 8 As shown, the second oil outlet passages 90, 90a, and 90b include a main oil outlet passage 91 and secondary oil outlet passages 92 and 93 located in the booster end cover 10 and the booster reversing valve body 20, respectively. Secondary oil outlet passage 92 is connected to the first chamber 40. One end of the main oil outlet passage 91 is connected to secondary oil outlet passage 92, and the other end is connected to secondary oil outlet passage 93. Secondary oil outlet passage 93 is connected to the second oil outlet valve 94.

[0058] Specifically, the inner diameter of the main oil outlet passage 91 is larger than that of the secondary oil outlet passage 92, which allows for a greater oil reserve through the main oil outlet passage 91.

[0059] The first oil inlet passage 60 is connected at one end to the first chamber 40 separated by the piston 30 of the booster device, and at the other end to the external hydraulic oil of the booster device; the first oil outlet passage 70 is connected at one end to the second chamber 50 separated by the piston 30 of the booster device, and at the other end to the external hydraulic oil of the booster device; the second oil outlet passages 90, 90a, and 90b are connected at one end to the first chamber 40, and at the other end to the external hydraulic oil of the booster device. The implementation process is as follows: When the piston 30 of the booster device moves in the first direction, external hydraulic oil enters the first chamber 40 through the first inlet passage 60. At this time, the oil in the second chamber 50 is discharged through the first outlet passage 70. When the piston 30 of the booster device moves in the second direction, which is opposite to the first direction, the hydraulic oil in the first chamber 40 is smoothly discharged through the second outlet passages 90, 90a, and 90b under the buffering effect of the second outlet passages 90, 90a, and 90b, thereby reducing oil pressure fluctuations. This application uses the second outlet passages 90, 90a, and 90b located between the end cover 10 and the reversing valve body 20. During the movement in the second direction, the hydraulic oil in the first chamber 40 is pre-output to the second outlet passages 90, 90a, and 90b, and then discharged through the second outlet passages 90, 90a, and 90b with a stable oil volume. Figure 11 As shown, the pressure fluctuation curve B after setting the second oil inlet passages 80, 80a, and 80b shows that, compared to the pressure fluctuation curve A, the frequency of pressure fluctuations between 12MPa and 15MPa is significantly reduced. The pressure fluctuations between peaks and valleys are smoother per unit time, reducing the "intenseness" of the pressure fluctuations and making the fluctuations between peaks and valleys smoother. This achieves stable oil input, alleviates the pressure sudden change during piston 30 switching, and reduces the pressure fluctuations generated when piston 30 of the booster device switches back and forth.

[0060] Example 4: This application refers to a booster pump 1000 that includes the oil inlet and outlet structure for the booster device described in Embodiment 3 above. For example... Figure 1 , Figure 2 , Figures 5-10 As shown, the booster pump 1000 includes an end cover 10 and a reversing valve body 20. The reversing valve body 20 of this application includes a pneumatic reversing valve 21, a piston rod 23, and a drive piston 22 located on one side of the piston rod 23. The pneumatic reversing valve 21 automatically switches the intake direction of compressed air, drives the drive piston 22 to reciprocate, and then drives the booster device piston 30 to move synchronously, so as to realize the reciprocating cycle of oil suction and oil discharge.

[0061] Among them, such as Figure 5 As shown, a cavity is provided between the end cap 10 and the reversing valve body 20. A booster piston 30 is provided in the cavity. The booster piston 30 is coaxially arranged with the drive piston 22 and located on the other side of the piston rod 23. The booster piston 30 divides the cavity into a first chamber 40 and a second chamber 50.

[0062] It also includes a first oil inlet passage 60 located on the end cover 10, a first oil outlet passage 70 located on the reversing valve body 20, and a second oil outlet passage 90, 90a, 90b located between the end cover 10 and the reversing valve body 20.

[0063] Among them, the second oil outlet passages 90, 90a, and 90b have larger diameters and a certain oil storage capacity. When the pneumatic control reversing valve 21 automatically switches the intake of compressed air, it can reduce the obvious pressure fluctuations that may easily occur when the piston 30 of the booster device switches back and forth.

[0064] The implementation process is as follows: When the pneumatic reversing valve 21 drives the driving piston 22 to move in the first direction, it drives the booster piston 30 to move in the same direction. At this time, external hydraulic oil is input into the first chamber 40 through the first oil inlet passage 60, and the oil in the second chamber 50 is discharged through the first oil outlet passage 70. When the pneumatically controlled directional valve 21 drives the piston 22 to move in the second direction, it drives the booster piston 30 to move in the same direction. The second direction is opposite to the first direction. At this time, external hydraulic oil is input into the second chamber 50 through the second oil inlet passages 80, 80a, and 80b located on the directional valve body 20. The oil in the first chamber 40 is discharged through the second oil outlet passages 90, 90a, and 90b located between the end cover 10 and the directional valve body 20, thereby realizing the oil suction and oil discharge cycle of the booster pump 1000. Using this booster pump 1000, the oil pressure fluctuation is small, which can adapt to the demanding working conditions such as high-precision pressure resistance testing and precision hydraulic molding, which have strict requirements for pressure stability. This application includes a booster pump 1000 with second oil outlet passages 90, 90a, and 90b. The second oil outlet passages 90, 90a, and 90b can provide a buffer for the oil discharged when the booster piston 30 moves in the second direction in the first chamber 40. Figure 11 As shown, after setting the second oil outlet passages 90, 90a, and 90b, the pressure fluctuation between peaks and valleys per unit time is smoother, which is suitable for working conditions with stringent requirements for pressure stability, such as high-precision pressure resistance testing and precision hydraulic forming.

[0065] The above embodiments merely illustrate several implementation methods of the present invention, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the invention patent. It should be noted that, for those skilled in the art, several modifications and improvements can be made without departing from the concept of the present invention. These are all equivalent modifications and improvements made to the above embodiments based on the essential technology of the present invention, and all of these fall within the protection scope of the present invention.

Claims

1. An oil inlet and outlet structure for a supercharging device, comprising a first oil inlet passage on an end cover of the supercharging device and a first oil outlet passage on a reversing valve body of the supercharging device, characterized in that: a second oil inlet passage is further arranged between the end cover and the reversing valve body; wherein: one end of the first oil inlet passage is connected to a first chamber separated by a piston of the supercharging device, and the other end of the first oil inlet passage is connected to external hydraulic oil of the supercharging device; one end of the first oil outlet passage is connected to a second chamber separated by the piston of the supercharging device, and the other end of the first oil outlet passage is connected to the external hydraulic oil of the supercharging device; one end of the second oil inlet passage is connected to the second chamber, and the other end of the second oil inlet passage is connected to the external hydraulic oil of the supercharging device; when the piston of the supercharging device moves in a first direction, the external hydraulic oil enters the first chamber through the first oil inlet passage, and at this time, oil in the second chamber is discharged through the first oil outlet passage; when the piston of the supercharging device moves in a second direction opposite to the first direction, the external hydraulic oil enters the second chamber gently under the buffering action of the second oil inlet passage, so as to reduce oil pressure fluctuation. An oil delivery pipeline is further arranged in the end cover of the supercharging device, and the oil delivery pipeline is in communication with the first oil inlet passage and the second oil inlet passage, respectively. The first oil inlet passage comprises a first oil inlet valve, the first oil inlet valve comprises a sealing element, a valve core and a return spring, an oil inlet through hole is arranged in the end cover of the supercharging device, the sealing element, the valve core and the return spring are sequentially arranged in the oil inlet through hole, the return spring abuts against the valve core and an end portion of the oil inlet through hole, respectively, and the sealing element seals a gap between the valve core and the oil inlet through hole. The valve core is a ball valve core. The second oil inlet pipeline extends from the end cover of the supercharging device to the reversing valve body of the supercharging device. The oil inlet and outlet structure for the supercharging device according to any one of claims 1-5 is included.

7. An oil inlet and outlet structure for a supercharging device, comprising a first oil inlet passage on an end cover of the supercharging device and a first oil outlet passage on a reversing valve body of the supercharging device, characterized in that: a second oil outlet passage is further arranged between the end cover and the reversing valve body; wherein: one end of the first oil inlet passage is connected to a first chamber separated by a piston of the supercharging device, and the other end of the first oil inlet passage is connected to external hydraulic oil of the supercharging device; one end of the first oil outlet passage is connected to a second chamber separated by the piston of the supercharging device, and the other end of the first oil outlet passage is connected to the external hydraulic oil of the supercharging device; one end of the second oil outlet passage is connected to the first chamber, and the other end of the second oil outlet passage is connected to the external hydraulic oil of the supercharging device; when the piston of the supercharging device moves in a first direction, the external hydraulic oil enters the first chamber through the first oil inlet passage, and at this time, oil in the second chamber is discharged through the first oil outlet passage; when the piston of the supercharging device moves in a second direction opposite to the first direction, hydraulic oil in the first chamber is discharged gently through the second oil outlet passage under the buffering action of the second oil outlet passage, so as to reduce oil pressure fluctuation.

2. The oil inlet / outlet structure for a supercharger according to claim 1, characterized by: The second oil outlet passage comprises a main oil outlet passage and a secondary oil outlet passage one and a secondary oil outlet passage two arranged in the end cover of the supercharging device and the reversing valve body of the supercharging device, respectively.

3. The oil inlet and outlet structure for a supercharger according to claim 1, characterized by: ​ 4. The oil inlet / outlet structure for a supercharger according to claim 3, characterized by: ​ 5. The oil inlet and outlet structure for a supercharger according to claim 1, characterized by: ​ 6. A booster pump characterized by: ​ ​ ​ ​ ​ ​ ​ ​ 8. The oil inlet / outlet structure for a supercharger according to claim 7, characterized by: ​ 9. The oil inlet / outlet structure for a supercharger according to claim 8, characterized by: The inner diameter of the main oil outlet passage is larger than the inner diameter of the secondary oil outlet passage.

10. A booster pump characterized by: Includes the oil inlet / outlet structure for a booster device as described in any one of claims 7 to 9.

Images