Pneumatic oil hydraulic pump with elastic dynamic seal

Abstract

The utility model relates to a kind of pneumatic oil pressure pumping with elastic dynamic sealing, it includes pump body, valve body and oil tank, overload protection device, first check valve core, second check valve core and spring, overload protection device is connected with valve body, it has ejector pin, ejector pin sliding fit in valve sleeve, first check valve core and second check valve core are located in valve sleeve, and are connected by spring, first step position and second step position should be formed on the inner peripheral wall of valve sleeve, oil outlet hole is located between first step position and second step position, the oil return channel of valve body is located in the side of second step position close to overload protection device, first check valve core and second check valve core are equipped with sealing ring, and are respectively through sealing ring and first step position and second step position interference resistance fit.This technical scheme can effectively absorb the energy of oil liquid impact by elastic deformation, to reduce cumulative wear, not only maintain stable sealing performance under dynamic condition, and significantly improve overall reliability.

Description

Technical Field

[0001] This utility model relates to the field of pump technology, and more specifically to a pneumatic hydraulic pump with an elastic dynamic seal. Background Technology

[0002] A pneumatic hydraulic pump is a power device that uses compressed air to drive hydraulic fluid to generate high pressure. It is widely used in industrial fields. The pneumatic hydraulic pump integrates a check valve, which plays two key roles: first, maintaining system pressure by preventing backflow of hydraulic fluid during the pneumatic piston's return stroke, ensuring stable output pressure; second, protecting the pneumatic system by preventing hydraulic fluid from entering the pneumatic pipeline and causing contamination. Currently, most mainstream pneumatic hydraulic pumps use steel balls as the check seal structure, such as the one disclosed in Chinese Patent No. CN212389486U, which has a spring-loaded... A pneumatic hydraulic pump with dynamic sealing includes a cylinder, a pump, and a piston. The pump includes an inlet check valve and an outlet check valve. The inlet check valve is installed at the lower end of the cylinder, and the outlet check valve is located on one side of the lower end cover of the cylinder. The inlet check valve includes an inlet valve body, an inlet channel, an inlet valve fixing component, an inlet valve core, and an inlet valve steel ball. The inlet valve steel ball is installed on the inlet valve core and is used to seal the inlet port. The outlet check valve includes an outlet valve body, an outlet channel, an outlet valve fixing component, an outlet valve core, and an outlet valve steel ball. The outlet valve steel ball is installed on the outlet valve core and is used to seal the outlet port.

[0003] The pneumatic hydraulic pump using the above-mentioned technical solution as an example uses steel balls as a check seal structure. Although it has advantages such as low cost and fast response, it has obvious technical defects in terms of sealing performance. The steel ball has a rigid linear contact with the oil inlet and outlet. Long-term high-speed impact of the oil will cause the steel ball to collide with the oil inlet and outlet, resulting in cumulative damage to the contact surface. This progressive wear will not only change the geometry of the contact surface, but will also eventually cause the steel ball sealing performance to deteriorate, thereby affecting the reliability of the entire pump. Utility Model Content

[0004] To address the above issues, and to overcome the problem that existing pneumatic and hydraulic pumps utilize steel balls as a check seal structure, where the steel balls collide with the inlet and outlet surfaces under long-term high-speed impact from the oil, leading to cumulative damage to the contact surfaces, deterioration of sealing performance, and impact on the overall pump reliability, the purpose of this invention is to provide a pneumatic and hydraulic pump that, through its elastic deformation compensation capability under long-term high-speed impact from the oil, effectively absorbs the energy of the oil impact, thereby reducing cumulative wear. This not only maintains stable sealing performance under dynamic operating conditions but also significantly improves overall reliability.

[0005] To achieve the above objectives, the technical solution of this utility model is:

[0006] A pneumatic-hydraulic pump with an elastic dynamic seal includes a pump body, a valve body, and an oil tank. The valve body is mounted on the pump body, and the oil tank is connected to the valve body. The valve body has a valve chamber, and its outer wall has an inlet channel, an outlet channel, and a return channel communicating with the valve chamber. The valve chamber is connected to the pump body and to the oil tank through the inlet and return channels. A valve sleeve is provided in the inlet channel, and an outlet hole is provided on the valve sleeve. The pump also includes an overload protection device, a first check valve core, a second check valve core, and a spring. The overload protection device and... The valve body is connected, and the overload protection device has a pin that slides inside the valve sleeve. The first check valve core and the second check valve core are located in the valve sleeve and are connected by a spring. The inner circumferential wall of the valve sleeve should have a first step and a second step. The oil outlet is located between the first step and the second step. The oil return channel is located on the side of the second step near the overload protection device. Both the first check valve core and the second check valve core are equipped with sealing rings and are respectively press-fitted with the first step and the second step through the sealing rings.

[0007] Preferably, a first sealing flange and a second sealing flange are formed on the first step and the second step, respectively, and the first check valve core and the second check valve core are respectively press-fitted with the first sealing flange and the second sealing flange through sealing rings.

[0008] Preferably, both the first sealing flange and the second sealing flange have a frustum-shaped cross section.

[0009] Preferably, an oil passage groove is provided on the outer wall of the valve sleeve, the oil outlet channel is opposite to the oil passage groove, and the oil outlet hole is opened in the oil passage groove.

[0010] Preferably, the valve sleeve has an internal flared section that is opposite to the pin of the overload protection device and whose shape matches the pin.

[0011] Preferably, a third step is formed on the outer wall of the valve sleeve, and a corresponding fourth step is formed on the inner wall of the valve chamber, with the third step and the fourth step abutting each other.

[0012] Preferably, the diameters of the first check valve core and the second check valve core are smaller than the inner diameter of the valve sleeve.

[0013] Preferably, the first check valve core and the second check valve core are respectively provided with a first limiting groove and a second limiting groove, and the two ends of the spring are respectively embedded in the first limiting groove and the second limiting groove.

[0014] Preferably, it also includes a pressure switch, which is located on the valve body.

[0015] Compared with the prior art, the advantages of this utility model are:

[0016] In this invention, both the first and second steps are annular. When they mate with the sealing rings of the first and second check valve cores, they form a continuous annular sealing surface. The sealing rings are made of elastic material, and their adaptive deformation capability can compensate for slight deviations between the first and second steps. This ensures that there is no leakage between the first and second check valve cores and their corresponding first and second steps in the initial state. Compared to the hard sealing method of steel ball check seals that relies on line contact, the elastic sealing rings effectively absorb the impact kinetic energy when subjected to high-speed oil impact, thereby reducing cumulative damage to the contact surface, extending the service life of the sealing rings, ensuring long-term stable sealing performance, and significantly improving the overall reliability of the pump. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the overall structure of the pump of this utility model;

[0018] Figure 2 This is a cross-sectional structural diagram of the pump of this utility model;

[0019] Figure 3 This is a utility model Figure 3 A magnified structural diagram of part A;

[0020] Figure 4 This is a utility model Figure 3 A schematic diagram of the structure when the first check valve core moves toward the center of the valve sleeve;

[0021] Figure 5 This is a utility model Figure 3 A schematic diagram of the structure when the second check valve core moves toward the center of the valve sleeve;

[0022] Figure 6 This is a schematic diagram of the overall structure of the first and second check valve cores of the pump connected by a spring in this utility model.

[0023] Figure 7 This is a schematic diagram of the overall structure of the pump valve sleeve of this utility model;

[0024] Figure 8 This is a cross-sectional structural diagram of the pump valve body of this utility model.

[0025] As shown in the figure:

[0026] 1. Pump body; 2. Valve body; 201. Valve chamber; 201a. Fourth step position; 202. Oil inlet channel; 203. Oil outlet channel; 204. Oil return channel; 3. Oil tank; 4. Valve sleeve; 401. Oil outlet hole; 403. First step position; 403a. First sealing flange; 404. Second step position; 404a. Second sealing flange; 405. Oil passage groove; 406. Flared section; 407. Third step position; 5. Overload protection device; 501. Pin; 6. First check valve core; 601. First limit groove; 7. Second check valve core; 701. Second limit groove; 8. Spring; 9. Sealing ring; 10. Pressure switch; 11. Piston. Detailed Implementation

[0027] The present invention will now be described in further detail with reference to the accompanying drawings and specific embodiments.

[0028] In the description of this utility model, it should be noted that the terms "upper", "lower", "left", "right", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship that the utility model product is usually placed in during use. They are only for the purpose of simplifying the description and do not indicate or imply that the orientation is a specific orientation or specific orientation structure and operation. Therefore, they should not be construed as limiting this utility model.

[0029] like Figures 1 to 7As shown, a pneumatic hydraulic pump with an elastic dynamic seal includes a pump body 1, a valve body 2, and an oil tank 3. A piston 11 is located in the pump body 1. The valve body 2 is mounted on the pump body 1, and the oil tank 3 is connected to the valve body 2. The valve body 2 has a valve chamber 201, and its outer wall has an inlet channel 202, an outlet channel 203, and a return channel 204. All three channels communicate with the valve chamber 201, which is connected to the pump body 1 and, through the inlet and return channels 202 and 204, to the oil tank 3. The valve chamber 201 also communicates with the hydraulic actuator of the hydraulic system through the outlet channel 203. A valve sleeve 4 is located in the inlet channel 202, and an outlet hole 401 is provided on the valve sleeve 4. When the piston in the pump body 1... During the reciprocating motion of pump 11, the pressure in pump body 1 and valve chamber 201 changes periodically. During the negative pressure phase, oil in tank 3 is drawn into pump body 1 through inlet channel 202. During the pressurization phase, oil is pumped to hydraulic actuators through outlet port 401 and outlet channel 203 of valve sleeve 4 to supply oil to the hydraulic actuators. Specifically, it also includes an overload protection device 5, a first check valve core 6, a second check valve core 7, and a spring 8. The overload protection device 5 is connected to valve body 2. Specifically, the overload protection device 5 and pump body 1 are located on the front and rear sides of valve body 2, respectively. The overload protection device 5 has a pin 501, which slides within valve sleeve 4. The first check valve core 6 and the second check valve core 7 are located within valve sleeve 4. The second check valve cores 7 have an axial clearance, allowing them to slide back and forth along the valve sleeve 4. The first check valve core 6 and the second check valve core 7 are opposite to the pump body 1 and the overload protection device 5, respectively, and are connected by a spring 8. The inner circumferential wall of the valve sleeve 4 should have a first step position 403 and a second step position 404. The oil outlet 401 is located between the first step position 403 and the second step position 404. The oil return channel 204 is located on the side of the second step position 404 near the overload protection device 5. Both the first check valve core 6 and the second check valve core 7 are provided with sealing rings 9. In the initial state and when a negative pressure is formed in the valve chamber 201, the first check valve core 6 and the second check valve core 7, under the support of the spring 8, are respectively connected to the first step position 403 and the second step position 404 by the sealing rings 9. The second step position 404 is interference-fitted to prevent oil from entering the oil outlet channel 203 and the oil return channel 204, thus avoiding internal leakage during the oil inlet process. When pressurized, under the action of high-pressure oil, the supporting force of the spring 8 is overcome, causing the first check valve core 6 to move towards the center of the valve sleeve 4, releasing the sealing fit with the first step position 403 and creating a gap, allowing oil to enter the interior of the valve sleeve 4 through this gap. The oil pressure acts on the side of the second check valve core 7 away from the second step position 404, and in conjunction with the elastic force of the spring 8 compression, increases the pressure between the second check valve core 7 and the second step position 404, preventing oil from entering the oil return channel 204. At this time, the oil can be pumped to the hydraulic actuator through the oil outlet 401 and the oil outlet channel 203 to supply oil to the hydraulic actuator.If the oil pressure in valve chamber 201 exceeds the threshold, the overload protection device 5's pin 501 can push the second check valve core 7, causing it to overcome the supporting force of spring 8 and move towards the center of valve sleeve 4. This releases the sealing fit with the second step position 404, creating a gap and opening the return oil passage 204. Since the oil pressure in valve sleeve 4 is greater than the oil pressure in pump chamber, under the action of oil pressure and spring 8, the first check valve core 6 will reset, causing its sealing ring 9 to re-mate with the first step position 403, preventing oil from entering the pump chamber. The oil will then be released to the oil tank 3 through the return oil passage 204, thus preventing mechanical failures such as seal failure due to excessive oil pressure. This ensures the continuous working capacity of the pump, extends its service life, and improves operational safety. It should also be mentioned that both the first step 403 and the second step 404 are annular, forming a continuous annular sealing surface when mated with the sealing ring 9. The sealing ring 9 is made of elastic material, and its self-adaptive deformation capability can compensate for minor deviations between itself and the first step 403 and the second step 404. This ensures a leak-free seal between the first check valve core 6 and the second check valve core 7 and their corresponding first step 403 and second step 404 in the initial state. Compared to the hard seal method relying on line contact, the elastic sealing ring 9 effectively absorbs the impact kinetic energy when subjected to high-speed oil impact, thereby reducing cumulative damage to the contact surface, extending the service life of the sealing ring 9, ensuring long-term stable sealing performance, and significantly improving the overall reliability of the pump.

[0030] like Figures 3 to 5 As shown, a first sealing flange 403a and a second sealing flange 404a are formed on the first step and the second step 404, respectively. In the initial state and when a negative pressure is formed in the valve chamber 201, the first check valve core 6 and the second check valve core 7 are press-fitted with the first sealing flange 403a and the second sealing flange 404a through the sealing ring 9, respectively. At this time, under the action of the first sealing flange 403a and the second sealing flange 404a, the corresponding lower sealing ring 9 will undergo elastic deformation, thereby forming a non-linear mating position with a labyrinth structure between it and the first sealing flange 403a and the second sealing flange 404a, further improving the sealing performance.

[0031] like Figures 3 to 5 As shown, the cross-sections of the first sealing flange 403a and the second sealing flange 404a are both frustoconical. When the first check valve core 6 and the second check valve core 7 are press-fitted with the first sealing flange 403a and the second sealing flange 404a respectively through the sealing ring 9, a gradual radial clamping force will be applied to the sealing ring 9, which can avoid local stress concentration and significantly improve the adaptability and durability of the seal.

[0032] like Figures 3 to 5 as well as Figure 8As shown, an oil passage groove 405 is provided on the outer wall of the valve sleeve 4, and the oil outlet channel 203 is opposite to the oil passage groove 405. The oil outlet hole 401 is opened in the oil passage groove 405. Based on the above configuration, a flow guide gap will be formed between the oil passage groove 405 of the valve sleeve 4 and the inner wall of the valve chamber 201 to prevent the oil outlet hole 401 from being blocked by the inner wall of the valve chamber 201, ensuring that the oil outlet hole 401 is unobstructed. Thus, when pumping oil, the oil can smoothly enter the valve chamber 201 through the oil outlet hole 401 and finally be pumped into the hydraulic actuator through the oil outlet channel 203. Preferably, the oil passage groove 405 is annular to ensure that when pumping oil, the oil enters the valve chamber 201 evenly and is then transported to the actuator through the oil outlet channel 203.

[0033] like Figures 3 to 5 as well as Figure 8 As shown, the valve sleeve 4 has a flared section 406 inside. The flared section 406 is opposite to the ejector pin 501 of the overload protection device 5. The ejector pin 501 is slidably fitted in the flared section 406, and the shape of the flared section 406 matches the ejector pin 501. The flared section 406 can limit the ejector pin 501 when it moves towards the center of the valve sleeve 4, effectively preventing the ejector pin 501 from exceeding the stroke limit.

[0034] like Figures 3 to 6 as well as Figure 8 As shown, a third step position 407 is formed on the outer wall of the valve sleeve 4, and a corresponding fourth step position 201a is formed on the inner wall of the valve chamber 201. The third step position 407 and the fourth step position 201a abut against each other. The valve sleeve 4 is quickly and accurately positioned and installed by the mutual mating of the step surfaces. It should be noted that there can be multiple third step positions 407. Multiple sets of mutual mating step surfaces constitute anti-misinstallation positioning, which provides multi-directional constraints while ensuring the rapid assembly of the valve sleeve 4 and improving the stability of the valve sleeve 4 at the rear end of the installation.

[0035] like Figures 3 to 5 As shown, the diameters of the first check valve core 6 and the second check valve core 7 are smaller than the inner diameter of the valve sleeve 4. This means that there is a gap between the first check valve core 6 and the second check valve core 7 and the inner circumferential wall of the valve sleeve 4. This gap allows the oil to smoothly enter between the first check valve core 6 and the second check valve core 7 and enter the return oil passage 204 from between the first check valve core 6 and the second check valve core 7 when the first check valve core 6 and the second check valve core 7 move towards the center of the valve sleeve 4, effectively preventing oil circuit blockage.

[0036] like Figures 3 to 5As shown, the first check valve core 6 and the second check valve core 7 are respectively provided with a first limiting groove 601 and a second limiting groove 701. The two ends of the spring 8 are respectively embedded in the first limiting groove 601 and the second limiting groove 701. The first limiting groove 601 and the second limiting groove 701 will axially limit the spring 8, so that the spring 8 maintains linear extension and contraction, ensuring that the elastic force is effectively transmitted to the first check valve core 6 and the second check valve core 7, and preventing fatigue bending, thereby extending the service life.

[0037] like Figure 1 and Figure 2 As shown, it also includes a pressure switch 10, which is located on the valve body 2. The pressure switch 10 can adjust the internal pressure of the pump of this utility model to avoid safety hazards caused by uneven internal pressure.

[0038] Combination Figures 1 to 8 When the pump of this utility model is pumped into the oil tank, the piston 11 inside the pump body 1 moves away from the valve body 2, creating a negative pressure inside the valve chamber 201 of the pump body 1 and the valve body 2. At this time, the oil in the oil tank 3 is drawn into the pump body 1 through the oil inlet channel 202. At this time, the first check valve core 6 and the second check valve core 7, supported by the spring 8, abut against the first step position 403 and the second step position 404 respectively through the sealing ring 9. When pumping oil, the internal pressure of the pump body 1 increases. Under the action of oil pressure, the first check valve core 6 will overcome the support of the spring 8. The force moves towards the center of the valve sleeve 4, releasing the sealing fit with the first step position 403 and creating a gap. This allows oil to pass through this gap and the first check valve core 6, entering between the first check valve core 6 and the second check valve core 7. At this time, the oil pressure acts on the side of the second check valve core 7 away from the second step position 404, and, in conjunction with the elastic force of the spring 8, increases the pressure between the second check valve core 7 and the second step position 404, preventing oil from entering the return oil channel 204. The oil entering the valve sleeve 4 will pass through the outlet... Oil enters through the guide gap between valve chamber 201 and the through channel via oil hole 401, and is finally pumped into the hydraulic actuator through oil outlet channel 203. Pressure switch 10 can adjust the internal pressure of valve chamber 201. If the oil pressure in valve chamber 201 exceeds the threshold, the second check valve core 7 can be pushed by the pin 501 of overload protection device 5, causing it to overcome the supporting force of spring 8 and move towards the center of valve sleeve 4, releasing the sealing fit with the second step position 404 and creating a gap, thereby opening the return oil channel 204 and the valve... The oil pressure inside sleeve 4 is greater than the oil pressure inside the pump chamber. Under the action of the oil pressure and the elastic force of spring 8, the first check valve core 6 will reset so that its sealing ring 9 abuts against the first step 403 again, preventing oil from entering the pump chamber. At this time, the oil will enter the return oil channel 204 through the gap between the second check valve core 7 and the inner peripheral wall of the valve sleeve 4 and be discharged to the oil tank 3, thereby avoiding mechanical failures such as seal failure caused by excessive oil pressure. While ensuring the continuous working capacity of the pump of this utility model, it also extends the service life and improves the operational safety.

[0039] The embodiments and descriptions above are merely illustrative of the principles and preferred embodiments of this utility model. Various changes and modifications may be made to this utility model without departing from its spirit and scope, and all such changes and modifications fall within the scope of this utility model as claimed.

Claims

1. A pneumatic hydraulic pump with elastic dynamic seal, comprising a pump body (1), a valve body (2), and an oil tank (3), wherein the valve body (2) is disposed on the pump body (1), the oil tank (3) is connected to the valve body (2), the valve body (2) has a valve chamber (201), and an oil inlet channel (202), an oil outlet channel (203), and a return oil channel (204) communicating with the valve chamber (201) are provided on the outer wall, the valve chamber (201) is communicating with the pump body (1), and is also communicating with the oil tank (3) through the oil inlet channel (202) and the return oil channel (204), wherein a valve sleeve (4) is provided in the oil inlet channel (202), and an oil outlet hole (401) is provided on the valve sleeve (4), characterized in that, It also includes an overload protection device (5), a first check valve core (6), a second check valve core (7), and a spring (8). The overload protection device (5) is connected to the valve body (2). The overload protection device (5) has a pin (501), which is slidably fitted inside the valve sleeve (4). The first check valve core (6) and the second check valve core (7) are located in the valve sleeve (4) and connected by the spring (8). The inner circumferential wall of the valve sleeve (4) should be formed with a first check valve core (6) and a second check valve core (7). The first step (403) and the second step (404) are provided. The oil outlet (401) is located between the first step (403) and the second step (404). The oil return channel (204) is located on the side of the second step (404) near the overload protection device (5). The first check valve core (6) and the second check valve core (7) are both provided with sealing rings (9), and are respectively press-fitted with the first step (403) and the second step (404) through the sealing rings (9).

2. A pneumatic hydraulic pump with an elastic dynamic seal according to claim 1, characterized in that, A first sealing flange (403a) and a second sealing flange (404a) are formed on the first step and the second step (404), respectively. The first check valve core (6) and the second check valve core (7) are respectively press-fitted with the first sealing flange (403a) and the second sealing flange (404a) through the sealing ring (9).

3. A pneumatic hydraulic pump with an elastic dynamic seal according to claim 2, characterized in that, The cross-sections of the first sealing flange (403a) and the second sealing flange (404a) are both frustum-shaped.

4. A pneumatic-hydraulic pump with an elastic dynamic seal according to any one of claims 1 to 3, characterized in that, An oil passage groove (405) is provided on the outer wall of the valve sleeve (4), the oil outlet channel (203) is opposite to the oil passage groove (405), and the oil outlet hole (401) is opened in the oil passage groove (405).

5. A pneumatic hydraulic pump with an elastic dynamic seal according to claim 4, characterized in that, The valve sleeve (4) has an internal flared section (406) which is opposite to the ejector pin (501) of the overload protection device (5) and whose shape matches the ejector pin (501).

6. A pneumatic-hydraulic pump with an elastic dynamic seal according to claim 5, characterized in that, A third step (407) is formed on the outer wall of the valve sleeve (4), and a corresponding fourth step (201a) is formed on the inner wall of the valve chamber (201). The third step (407) and the fourth step (201a) are matched.

7. A pneumatic hydraulic pump with an elastic dynamic seal according to any one of claims 1, 2, 3, 5 or 6, characterized in that, The diameters of the first check valve core (6) and the second check valve core (7) are smaller than the internal diameter of the valve sleeve (4).

8. A pneumatic hydraulic pump with an elastic dynamic seal according to claim 7, characterized in that, The first check valve core (6) and the second check valve core (7) are respectively provided with a first limiting groove (601) and a second limiting groove (701), and the two ends of the spring (8) are respectively embedded in the first limiting groove (601) and the second limiting groove (701).

9. A pneumatic hydraulic pump with an elastic dynamic seal according to any one of claims 1, 2, 3, 5, 6 or 8, characterized in that, It also includes a pressure switch (10) which is located on the valve body (2).

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