Filling pump swing valve main control oil way system and control method
By designing the main control oil circuit system of the filling pump in the filling pump, the combination of bypass valve and pressure reducing valve is used to solve the problem of mechanical impact in the reversing process of the S-swing valve, and the effect of self-flow filling and reducing mechanical impact is achieved.
Patent Information
- Application Number
- CN202510236464.0
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-02-28
- Publication Date
- 2025-06-24
AI Technical Summary
In the filling pump, the large S-swing valve swings due to its own weight during the reversing process, causing a passively stretched swing valve cylinder to cause a mechanical impact during the reversing process.
A filling pump swing valve main control oil circuit system is designed, and a bypass valve and pressure reducing valve are added. The pre-pressure is controlled through the bypass valve and the pressure reducing valve to eliminate the impact of the ball head of the swing cylinder on the ball socket.
When the filling pump stops filling operation, the self-flow filling of the pendulum valve oil pump is realized, eliminating the spacing between the pendulum valve oil cylinder and the support seat, and avoiding mechanical impact.
Smart Images
Figure CN120194054A_ABST
Abstract
Description
Technical Field
[0001] The invention belongs to the technical field of filling pump control systems, and particularly relates to a main control oil circuit system and a control method for a swing valve of a filling pump. Background Art
[0002] In a filling pump, due to the large self-weight of a large S swing valve, under normal circumstances, when the S swing valve swings into place, at this time the electro-hydraulic change valve is in the left position or the right position, and the accumulator pressure acts on one of the oil cylinders. At this time, the position of the S swing valve is determined and stable. When the electro-hydraulic reversing valve receives a reversing signal, because it takes time for the electro-hydraulic change valve to reverse, during the reversing process, due to the self-weight of the S swing valve, it will swing downward, resulting in the passive stretching of the compressed swing valve oil cylinder, so that a gap is generated between the end of this swing valve oil cylinder and the support seat. When the electro-hydraulic reversing valve reverses, the passively stretched oil cylinder will be compressed, thus causing a large mechanical impact between the end and the support seat. Summary of the Invention
[0003] The invention aims to overcome the deficiencies of the prior art and provides a main control oil circuit system and a control method for a swing valve of a filling pump.
[0004] In order to achieve the above object, the technical solution provided by the invention is as follows: The main control oil circuit system of the filling pump swing valve includes an A swing valve oil cylinder (1) and a B swing valve oil cylinder (2) arranged oppositely. The main control oil circuit system of the filling pump swing valve further includes an electro-hydraulic reversing valve composed of a first electro-hydraulic reversing valve (3) and a second electro-hydraulic reversing valve (4). The main control oil circuit system of the filling pump swing valve further includes a bypass valve (5) and a pressure reducing valve (6); the oil port of the A swing valve oil cylinder (1) is connected to the first oil port AA in the middle of the second electro-hydraulic reversing valve (4), and the third oil port AC in the middle of the second electro-hydraulic reversing valve (4) is connected to the third oil port BC in the middle of the first electro-hydraulic reversing valve (3); the oil port of the B swing valve oil cylinder (2) is connected to the second oil port AB in the middle of the second electro-hydraulic reversing valve (4), and the fourth oil port AD in the middle of the second electro-hydraulic reversing valve (4) is connected to the fourth oil port BD in the middle of the first electro-hydraulic reversing valve (3); the first oil port BA in the middle of the first electro-hydraulic reversing valve (3) is connected to the fifth oil port AE at one end of the second electro-hydraulic reversing valve (4), and the second oil port BB in the middle of the first electro-hydraulic reversing valve (3) is connected to the sixth oil port AF at the other end of the second electro-hydraulic reversing valve (4); the fourth oil port AD in the middle of the second electro-hydraulic reversing valve (4) is also connected to the first oil tank (7); the oil pipeline connecting the oil port of the A swing valve oil cylinder (1) to the first oil port AA of the second electro-hydraulic reversing valve (4) is connected to the first oil port CA of the bypass valve (5), the oil pipeline connecting the oil port of the B swing valve oil cylinder (2) to the second oil port AB of the second electro-hydraulic reversing valve (4) is connected to the second oil port CB of the bypass valve (5), the third oil port CC of the bypass valve (5) is connected to the first oil port DA of the pressure reducing valve (6), and the fourth oil port DD of the bypass valve (5) is connected to the second oil tank (8); the second oil port DB of the pressure reducing valve (6) is connected to the third oil port BC of the first electro-hydraulic reversing valve (3), and the second oil port DB of the pressure reducing valve (6) is also connected to the third oil port AC of the second electro-hydraulic reversing valve (4); the oil pipeline connecting the third oil port CC of the bypass valve (5) to the first oil port DA of the pressure reducing valve (6) is connected to the third oil port DC of the pressure reducing valve (6).
[0005] Preferably, the fifth oil port AE is close to the second oil port BB, and the sixth oil port AF is close to the first oil port AA.
[0006] Preferably, both ends of the first electro-hydraulic reversing valve (3) are blind ends, and both ends of the bypass valve (5) are blind ends.
[0007] Preferably, a valve is provided on the oil pipeline connecting the second oil port DB of the pressure reducing valve (6) to the third oil port AC of the second electro-hydraulic reversing valve (4).
[0008] Preferably, the oil pipeline connecting the fourth oil port AD of the second electro-hydraulic reversing valve (4) to the first oil tank (7) is connected to the second oil port DB of the pressure reducing valve (6), and a valve is provided on this oil pipeline.
[0009] Preferably, a pressure gauge (9), an accumulator (10), a direct-acting overflow valve (11) and a manual unloading valve (12) are also connected to the oil pipeline of the main control oil circuit system of the filling pump swing valve.
[0010] The swing valve control method based on the above-mentioned main control oil circuit system of the filling pump swing valve is as follows: when the filling pump normally stops the filling operation, under the action of the electro-hydraulic reversing valve, one of the two opposite swing valve cylinders is fully extended and the other is fully compressed. Manually operate the bypass valve to make the bypass valve convey oil to the swing valve cylinder, control the oil volume in the two swing valve cylinders, and thus control the position of the swing valve. When the swing valve is controlled to be in the middle position, the filling pipeline is connected to the filling pump hopper to achieve self-flow filling.
[0011] The following further explains the present invention: In the present invention, a bypass valve is added to the control loop of the swing valve cylinder, and a pressure reducing valve is added to the bypass loop of the swing valve cylinder to control the pre-pressure of the swing cylinder ball head. When the filling pump normally stops the pumping operation, one of the swing valve cylinders is fully extended and the other is fully compressed. At this time, the filling pipeline is connected to the delivery cylinder (self-flow filling cannot be achieved. When the filling multiple line fully meets the customer's requirement for self-flow, the self-flow method is adopted).
[0012] When the filling pump is normally pumping, the commutation is controlled by the right electro-hydraulic reversing valve. Before the electro-hydraulic reversing valve commutes, the bypass valve commutes in advance to pre-pressurize the swing valve cylinder at low pressure and eliminate the impact of the swing cylinder ball head on the ball socket. At the same time, for some working conditions where self-flow filling is possible, this bypass valve is used to control the stop position of the swing valve to achieve self-flow filling.
[0013] That is, through the present invention, self-flow filling can be achieved. When the filling operation is normally stopped, under the action of the electro-hydraulic reversing valve, one of the swing valve oil pumps is fully extended and the other is fully compressed. At this time, manually operate the bypass valve, and the swing valve cylinder can be in any position. When the S swing valve is in the middle position, the filling pipeline is connected to the filling pump hopper, thereby achieving self-flow filling.
[0014] In addition, the present invention can also eliminate the impact on the support ball socket when the swing valve cylinder commutes. Eliminate the gap between the swing valve cylinder and the support seat. After one of the swing valve cylinders is fully extended and the other is fully compressed, make the bypass valve in the left position or the right position (specifically, whether it is the left position or the right position depends on the debugging situation). Due to the action of the pressure reducing valve, low-pressure oil enters the oil inlet end of the pressure valve cylinder. Due to the action of this low-pressure oil when the electro-hydraulic reversing valve commutes, the gap between the swing valve cylinder and the support seat caused by the self-weight of the S valve is eliminated, thereby eliminating the mechanical impact generated when the electro-hydraulic reversing valve commutes. Brief Description of the Drawings
[0015] Figure 1 It is a schematic structural diagram of the present invention.
[0016] In the figure: 1. A swing valve oil cylinder; 2. B swing valve oil cylinder; 3. First electro-hydraulic reversing valve; 4. Second electro-hydraulic reversing valve; 5. Bypass valve; 6. Pressure reducing valve; 7. First oil tank; 8. Second oil tank; 9. Pressure gauge; 10. Accumulator; 11. Direct-acting overflow valve; 12. Manual unloading valve. Specific implementation mode
[0017] The present invention will be further described below in conjunction with the accompanying drawings and embodiments. Embodiment 1
[0018] See Figure 1 , the main control oil circuit system of the filling pump swing valve includes an A swing valve oil cylinder 1 and a B swing valve oil cylinder 2 arranged oppositely. The main control oil circuit system of the filling pump swing valve also includes an electro-hydraulic reversing valve composed of a first electro-hydraulic reversing valve 3 and a second electro-hydraulic reversing valve 4. The main control oil circuit system of the filling pump swing valve also includes a bypass valve 5 and a pressure reducing valve 6; the oil port of the A swing valve oil cylinder 1 is connected to the first oil port AA in the middle of the second electro-hydraulic reversing valve 4, and the third oil port AC in the middle of the second electro-hydraulic reversing valve 4 is connected to the third oil port BC in the middle of the first electro-hydraulic reversing valve 3; the oil port of the B swing valve oil cylinder 2 is connected to the second oil port AB in the middle of the second electro-hydraulic reversing valve 4, and the fourth oil port AD in the middle of the second electro-hydraulic reversing valve 4 is connected to the fourth oil port BD in the middle of the first electro-hydraulic reversing valve 3; the first oil port BA in the middle of the first electro-hydraulic reversing valve 3 is connected to the fifth oil port AE at one end of the second electro-hydraulic reversing valve 4, and the second oil port BB in the middle of the first electro-hydraulic reversing valve 3 is connected to the sixth oil port AF at the other end of the second electro-hydraulic reversing valve 4; the fourth oil port AD in the middle of the second electro-hydraulic reversing valve 4 is also connected to the first oil tank 7; the oil pipeline connecting the oil port of the A swing valve oil cylinder 1 to the first oil port AA of the second electro-hydraulic reversing valve 4 is connected to the first oil port CA of the bypass valve 5, and the oil pipeline connecting the oil port of the B swing valve oil cylinder 2 to the second oil port AB of the second electro-hydraulic reversing valve 4 is connected to the second oil port CB of the bypass valve 5. The third oil port CC of the bypass valve 5 is connected to the first oil port DA of the pressure reducing valve 6, and the fourth oil port DD of the bypass valve 5 is connected to the second oil tank 8; the second oil port DB of the pressure reducing valve 6 is connected to the third oil port BC of the first electro-hydraulic reversing valve 3, and the second oil port DB of the pressure reducing valve 6 is also connected to the third oil port AC of the second electro-hydraulic reversing valve 4; the oil pipeline connecting the third oil port CC of the bypass valve 5 to the first oil port DA of the pressure reducing valve 6 is connected to the third oil port DC of the pressure reducing valve 6.
[0019] Among them, the fifth oil port AE is close to the second oil port BB, and the sixth oil port AF is close to the first oil port AA.
[0020] Both ends of the first electro-hydraulic reversing valve 3 are blind ends, and both ends of the bypass valve 5 are blind ends.
[0021] A valve is provided on the oil pipeline connecting the second oil port DB of the pressure reducing valve 6 and the third oil port AC of the second electro-hydraulic directional valve 4.
[0022] The oil pipeline connecting the fourth oil port AD of the second electro-hydraulic directional valve 4 and the first oil tank 7 is connected to the second oil port DB of the pressure reducing valve 6, and a valve is provided on this oil pipeline.
[0023] A pressure gauge 9, an accumulator 10, a direct-acting relief valve 11 and a manual unloading valve 12 are also connected to the oil pipeline of the main control oil circuit system of the filling pump swing valve. Embodiment 2
[0024] Based on the swing valve control method of the main control oil circuit system of the filling pump described in Embodiment 1: When the filling pump normally stops the filling operation, under the action of the electro-hydraulic directional valve, one of the two opposite swing valve cylinders is fully extended and the other is fully compressed (the electro-hydraulic directional valve will be subjected to a pressure of about 20 Mpa). Manually operate the bypass valve to make the bypass valve deliver oil to the swing valve cylinder, provide a small counteracting pressure to reduce the impact, control the oil volume in the two swing valve cylinders, thereby controlling the position of the swing valve, eliminating the gap between the swing valve cylinder and the support seat. When the swing valve is controlled to be in the middle position, the filling pipeline is connected to the filling pump hopper to achieve self-flow filling; after achieving self-flow filling, only rely on the control of the bypass valve.
Claims
1. A filling pump swing valve main control oil circuit system, characterized in that: The filling pump swing valve main control oil circuit system comprises an A swing valve oil cylinder (1) and a B swing valve oil cylinder (2) which are arranged relatively to each other, the filling pump swing valve main control oil circuit system also comprises an electro-hydraulic reversing valve composed of a first electro-hydraulic reversing valve (3) and a second electro-hydraulic reversing valve (4), the filling pump swing valve main control oil circuit system also comprises a bypass valve (5) and a pressure reducing valve (6); the oil port of the A swing valve oil cylinder (1) is connected to the first oil port AA in the middle of the second electro-hydraulic reversing valve (4), and the third oil port in the middle of the second electro-hydraulic reversing valve (4) is connected to the third oil port AA in the middle of the second electro-hydraulic reversing valve (4). The oil port AC is connected to the third oil port BC in the middle of the first electro-hydraulic reversing valve (3); the oil port of the B swing valve cylinder (2) is connected to the second oil port AB in the middle of the second electro-hydraulic reversing valve (4); the fourth oil port AD in the middle of the second electro-hydraulic reversing valve (4) is connected to the fourth oil port BD in the middle of the first electro-hydraulic reversing valve (3); the first oil port BA in the middle of the first electro-hydraulic reversing valve (3) is connected to the fifth oil port AE at one end of the second electro-hydraulic reversing valve (4); the second oil port BB in the middle of the first electro-hydraulic reversing valve (3) is connected to the fifth oil port AE at one end of the second electro-hydraulic reversing valve (4); the The oil pipe connecting the oil port of the A swing valve cylinder (1) to the first oil port AA of the second electro-hydraulic reversing valve (4) is connected to the first oil port CA of the bypass valve (5); the oil pipe connecting the oil port of the B swing valve cylinder (2) to the second oil port AB of the second electro-hydraulic reversing valve (4) is connected to the second oil port CB ... A swing valve cylinder (1) to the first oil port AA of the second electro-hydraulic reversing valve (4) is connected to the second oil port CB of the bypass valve (5); the oil pipe connecting the oil port of the B swing valve cylinder (2) to the second oil port AB of the second electro-hydraulic reversing valve (4) is connected to the second oil port CB of the bypass valve (5); the oil pipe connecting the oil port of the The third oil port CC is connected to the first oil port DA of the pressure reducing valve (6), and the fourth oil port DD of the bypass valve (5) is connected to the second oil tank (8); the second oil port DB of the pressure reducing valve (6) is connected to the third oil port BC of the first electro-hydraulic reversing valve (3), and the second oil port DB of the pressure reducing valve (6) is also connected to the third oil port AC of the second voltage reversing valve (4); and the oil pipeline connecting the third oil port CC of the bypass valve (5) and the first oil port DA of the pressure reducing valve (6) is connected to the third oil port DC of the pressure reducing valve (6).
2. The filling pump swing valve main control oil circuit system according to claim 1, characterized in that: The fifth oil port AE is close to the second oil port BB, and the sixth oil port AF is close to the first oil port AA.
3. The filling pump swing valve main control oil circuit system according to claim 1, characterized in that: Both ends of the first electro-hydraulic reversing valve (3) are blind ends, and both ends of the bypass valve (5) are blind ends.
4. The filling pump swing valve main control oil circuit system according to claim 1, characterized in that: A valve is provided on the oil pipeline connecting the second oil port DB of the pressure reducing valve (6) and the third oil port AC of the second voltage reversing valve (4).
5. The filling pump swing valve main control oil circuit system according to claim 1, characterized in that: The oil pipeline connecting the fourth oil port AD of the second voltage reversing valve (4) and the first oil tank (7) is connected to the second oil port DB of the pressure reducing valve (6), and a valve is provided on the oil pipeline.
6. The filling pump swing valve main control oil circuit system according to claim 1, characterized in that: The oil pipeline of the main control oil system of the charging pump swing valve is also connected to a pressure gauge (9), an energy accumulator (10), a direct-acting overflow valve (11) and a manual unloading valve (12).
7. A swing valve control method for a filling pump swing valve main control oil circuit system according to any one of claims 1 to 6, characterized in that: The method is as follows: when the filling pump stops the filling operation normally, under the action of the electro-hydraulic reversing valve, one of the two relative swing valve cylinders is fully extended and the other is fully compressed, and the bypass valve is manually operated to make the bypass valve transport oil to the swing valve cylinder, and the amount of oil in the two swing valve cylinders is controlled, thereby controlling the position of the swing valve, and when the swing valve is controlled to be in the middle position, the filling pipeline is connected to the filling pump hopper to achieve gravity filling.