Main control oil way system of swing valve of filling pump
By introducing a control oil circuit system consisting of an A-swing valve cylinder, a B-swing valve cylinder, an electro-hydraulic directional valve, and a bypass pressure reducing valve into the filling pump, the mechanical impact problem caused by the weight of the large S-swing valve during the reversing process was solved, thus achieving gravity filling and stable operation of the equipment.
Patent Information
- Application Number
- CN202520343990.2
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-02-28
- Publication Date
- 2025-12-30
- Estimated Expiration
- 2035-02-28
AI Technical Summary
During the reversing process, the large S-shaped swing valve causes mechanical impact between the cylinder and the support seat due to its own weight, affecting the stability and service life of the equipment.
A control oil circuit system is adopted, which includes A swing valve cylinder, B swing valve cylinder, electro-hydraulic directional valve, bypass valve and pressure reducing valve. The position and pressure of the swing valve cylinder are controlled by the cooperation of the bypass valve and pressure reducing valve to eliminate mechanical impact.
It effectively eliminates the mechanical impact between the swing valve cylinder and the support seat, realizes self-flowing filling and stable operation of the equipment, and extends the service life of the equipment.
Smart Images
Figure CN223739749U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The utility model belongs to filling pump control system technical field, concretely relates to a filling pump swing valve main control oil circuit system. BACKGROUND
[0002] In the filling pump, the large S swing valve is heavy due to its own weight, under normal circumstances, when the S swing valve is in place, the electro-hydraulic valve is in the left or right position at this time, the energy storage device pressure acts on one of the oil cylinders, at this time, the S swing valve position is determined and stable, when the electro-hydraulic reversing valve receives the reversing signal, due to the time required for the electro-hydraulic valve to reverse, the S swing valve will swing downward due to its own weight during the reversing process, resulting in the compressed swing valve cylinder being passively in the stretched state, thereby causing the gap between the swing valve cylinder end and the support seat, when the electro-hydraulic reversing valve reverses, the passive stretched oil cylinder will be pressed, thereby causing the end and the support seat to produce a large mechanical impact. SUMMARY
[0003] The utility model aims at overcoming the prior art's insufficient, provides a filling pump swing valve main control oil circuit system.
[0004] In order to achieve the above-mentioned purpose, the technical scheme provided by the utility model is:
[0005] The filling pump swing valve main control oil circuit system comprises oppositely arranged A swing valve oil cylinder (1) and B swing valve oil cylinder (2), further comprises an electro-hydraulic reversing valve composed of a first electro-hydraulic reversing valve (3) and a second electro-hydraulic reversing valve (4), and further comprises a bypass valve (5) and a pressure reducing valve (6); the oil port of the A swing valve oil cylinder (1) is connected with the first oil port AA in the middle of the second electro-hydraulic reversing valve (4), the third oil port AC in the middle of the second electro-hydraulic reversing valve (4) is connected with 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 with 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 with 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 with 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 with 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 further connected with the first oil tank (7); the oil circuit pipeline connected with the first oil port AA of the second electro-hydraulic reversing valve (4) of the oil port of the A swing valve oil cylinder (1) is connected with the first oil port CA of the bypass valve (5), the oil circuit pipeline connected with the second oil port AB of the second electro-hydraulic reversing valve (4) of the oil port of the B swing valve oil cylinder (2) is connected with the second oil port CB of the bypass valve (5), the third oil port CC of the bypass valve (5) is connected with the first oil port DA of the pressure reducing valve (6), and the fourth oil port DD of the bypass valve (5) is connected with the second oil tank (8); the second oil port DB of the pressure reducing valve (6) is connected with 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 further connected with the third oil port AC of the second electro-hydraulic reversing valve (4); the oil circuit pipeline connected with the first oil port DA of the pressure reducing valve (6) of the third oil port CC of the bypass valve (5) is connected with the third oil port DC of the pressure reducing valve (6).
[0006] 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.
[0007] 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.
[0008] Preferably, a valve is arranged on the oil circuit pipeline connected with the second oil port DB of the pressure reducing valve (6) and the third oil port AC of the second electro-hydraulic reversing valve (4).
[0009] Preferably, a valve is arranged on the oil circuit pipeline connected with the fourth oil port AD of the second electro-hydraulic reversing valve (4) and the first oil tank (7), and the oil circuit pipeline is connected with the second oil port DB of the pressure reducing valve (6).
[0010] Preferably, the filling pump swing valve main control oil circuit system is further connected with a pressure gauge (9), an accumulator (10), a direct-acting overflow valve (11) and a manual pressure relief valve (12) on the oil circuit pipeline of the system.
[0011] The swing valve control method based on the filling pump swing valve main control oil circuit system is as follows: when the filling pump normally stops the filling operation, one of the two swing valve oil cylinders is completely extended and the other is completely compressed under the action of the electro-hydraulic reversing valve, the bypass valve is manually operated to control the oil amount in the two swing valve oil cylinders, thereby controlling the position of the swing valve, and when the swing valve is in the middle position, the filling pipeline is connected with the filling pump hopper to realize self-flow filling.
[0012] The utility model will be further described as follows:
[0013] In the utility model, a bypass valve is added to the swing valve oil cylinder control circuit, and a pressure reducing valve is added to the swing valve oil cylinder bypass circuit 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 oil cylinders is completely extended and the other is completely compressed, at which time the filling pipeline is connected with the delivery cylinder (self-flow filling cannot be realized when the filling times completely meet the self-flow requirement of the customer).
[0014] When the filling pump normally pumps, the right electro-hydraulic reversing valve controls the reversing, and the bypass valve reverses in advance before the electro-hydraulic pressure reversing valve reverses, so that the swing valve oil cylinder is pre-pressed at low pressure to eliminate the impact of the swing cylinder oil cylinder ball head on the ball socket. At the same time, the bypass valve is used to control the stop position of the swing valve for some self-flow filling conditions to realize self-flow filling.
[0015] That is, self-flow filling can be realized by the utility model. When the filling operation is normally stopped, one of the swing valve oil pumps is completely extended and the other is completely compressed under the action of the electro-hydraulic reversing valve, at which time the bypass valve is manually operated to make the swing valve oil cylinder be at any position, and when the swing valve is in the middle position, the filling pipeline is connected with the filling pump hopper to realize self-flow filling.
[0016] In addition, the utility model can also eliminate the impact of the swing valve oil cylinder reversing on the support ball socket. The interval between the swing valve oil cylinder and the support seat is eliminated, and when one of the swing valve oil cylinders is completely extended and the other is completely compressed, the bypass valve is in the left position or the right position (whether the left position or the right position is determined according to the debugging condition). Due to the action of the pressure reducing valve, low-pressure oil enters the oil inlet end of the compressed valve oil cylinder, and thus the interval between the swing valve oil cylinder and the support seat due to the self-weight of the S valve is eliminated under the action of the low oil when the electro-hydraulic pressure reversing valve reverses, thereby eliminating the mechanical impact generated when the electro-hydraulic reversing valve reverses. BRIEF DESCRIPTION OF DRAWINGS
[0017] Figure 1 The utility model is a structural schematic view.
[0018] 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. DETAILED DESCRIPTION
[0019] The utility model will be further explained in connection with the drawings and examples. Example 1
[0020] Referring to Figure 1 The filling pump swing valve main control oil circuit system comprises oppositely arranged A swing valve oil cylinder 1 and B swing valve oil cylinder 2, further comprises electro-hydraulic reversing valve composed of first electro-hydraulic reversing valve 3 and second electro-hydraulic reversing valve 4, and further comprises bypass valve 5 and pressure reducing valve 6; the oil port of A swing valve oil cylinder 1 is connected with the first oil port AA in the middle of second electro-hydraulic reversing valve 4, the third oil port AC in the middle of second electro-hydraulic reversing valve 4 is connected with the third oil port BC in the middle of first electro-hydraulic reversing valve 3; the oil port of B swing valve oil cylinder 2 is connected with the second oil port AB in the middle of second electro-hydraulic reversing valve 4, and the fourth oil port AD in the middle of second electro-hydraulic reversing valve 4 is connected with the fourth oil port BD in the middle of first electro-hydraulic reversing valve 3; the first oil port BA in the middle of first electro-hydraulic reversing valve 3 is connected with the fifth oil port AE at one end of second electro-hydraulic reversing valve 4, and the second oil port BB in the middle of first electro-hydraulic reversing valve 3 is connected with the sixth oil port AF at the other end of second electro-hydraulic reversing valve 4; the fourth oil port AD in the middle of second electro-hydraulic reversing valve 4 is further connected with first oil tank 7; the oil circuit pipeline connected with the first oil port AA of second electro-hydraulic reversing valve 4 of the oil port of A swing valve oil cylinder 1 is connected with the first oil port CA of bypass valve 5, the oil circuit pipeline connected with the second oil port AB of second electro-hydraulic reversing valve 4 of the oil port of B swing valve oil cylinder 2 is connected with the second oil port CB of bypass valve 5, the third oil port CC of bypass valve 5 is connected with the first oil port DA of pressure reducing valve 6, and the fourth oil port DD of bypass valve 5 is connected with second oil tank 8; the second oil port DB of pressure reducing valve 6 is connected with the third oil port BC of first electro-hydraulic reversing valve 3, and the second oil port DB of pressure reducing valve 6 is further connected with the third oil port AC of second electro-hydraulic reversing valve 4; the oil circuit pipeline connected with the first oil port DA of pressure reducing valve 6 of the third oil port CC of bypass valve 5 is connected with the third oil port DC of pressure reducing valve 6.
[0021] Wherein, 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.
[0022] The two ends of first electro-hydraulic reversing valve 3 are blind ends, and the two ends of bypass valve 5 are blind ends.
[0023] The oil line pipe connected between the second oil port DB of the pressure reducing valve 6 and the third oil port AC of the second voltage reversing valve 4 is provided with a valve.
[0024] The oil line pipe connected between the fourth oil port AD of the second voltage reversing valve 4 and the first oil tank 7 is connected with the second oil port DB of the pressure reducing valve 6, and the oil line pipe is provided with a valve.
[0025] The oil line pipe of the swing valve main control oil line system of the filling pump is further connected with a pressure gauge 9, an accumulator 10, a direct-acting overflow valve 11 and a manual pressure relief valve 12.
[0026] The swing valve control method based on the swing valve main control oil line system of the filling pump is as follows: when the filling pump is normally stopped, one of the two swing valve oil cylinders is completely extended and the other is completely compressed under the action of the electro-hydraulic reversing valve (the electro-hydraulic reversing valve will be subjected to a pressure of about 20 MPa), the bypass valve is manually operated to make the bypass valve deliver oil to the swing valve oil cylinder, provide a small counter-impact pressure to reduce impact, control the oil amount in the two swing valve oil cylinders, thereby controlling the position of the swing valve, eliminating the gap between the swing valve oil cylinder and the support seat, when the swing valve is controlled to be in the middle position, the filling pipeline is communicated with the hopper of the filling pump to realize self-flow filling; after the self-flow filling is realized, only the bypass valve control is needed.
Claims
1. A fill pump swing valve main control oil passage system characterized by, The filling pump swing valve main control oil circuit system comprises oppositely arranged A swing valve oil cylinder (1) and B swing valve oil cylinder (2), and further comprises an electro-hydraulic reversing valve composed of a first electro-hydraulic reversing valve (3) and a second electro-hydraulic reversing valve (4), a bypass valve (5) and a pressure reducing valve (6); the oil port of the A swing valve oil cylinder (1) is connected with a first oil port AA in the middle of the second electro-hydraulic reversing valve (4), a third oil port AC in the middle of the second electro-hydraulic reversing valve (4) is connected with a 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 with a second oil port AB in the middle of the second electro-hydraulic reversing valve (4), a fourth oil port AD in the middle of the second electro-hydraulic reversing valve (4) is connected with a fourth oil port BD in the middle of the first electro-hydraulic reversing valve (3); a first oil port BA in the middle of the first electro-hydraulic reversing valve (3) is connected with a fifth oil port AE at one end of the second electro-hydraulic reversing valve (4), a second oil port BB in the middle of the first electro-hydraulic reversing valve (3) is connected with a 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 further connected with a first oil tank (7); the oil circuit pipeline connected with the first oil port AA of the second electro-hydraulic reversing valve (4) of the oil port of the A swing valve oil cylinder (1) is connected with a first oil port CA of the bypass valve (5), the oil circuit pipeline connected with the second oil port AB of the second electro-hydraulic reversing valve (4) of the oil port of the B swing valve oil cylinder (2) is connected with a second oil port CB of the bypass valve (5), a third oil port CC of the bypass valve (5) is connected with a first oil port DA of the pressure reducing valve (6), a fourth oil port DD of the bypass valve (5) is connected with a second oil tank (8); a second oil port DB of the pressure reducing valve (6) is connected with 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 further connected with the third oil port AC of the second electro-hydraulic reversing valve (4); the oil circuit pipeline connected with the first oil port DA of the pressure reducing valve (6) of the third oil port CC of the bypass valve (5) is connected with a third oil port DC of the pressure reducing valve (6).
2. The main control oil passage system for a swing valve of a filling pump according to claim 1, wherein 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 main control oil circuit system of a swing valve of a filling pump according to claim 1, wherein 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 fill pump swing valve main control oil passage system of claim 1 wherein, A valve is arranged on the oil circuit pipeline connected with the second oil port DB of the pressure reducing valve (6) and the third oil port AC of the second electro-hydraulic reversing valve (4).
5. The fill pump swing valve main control oil passage system of claim 1 wherein, The oil circuit pipeline connected with the fourth oil port AD of the second electro-hydraulic reversing valve (4) and the first oil tank (7) is connected with the second oil port DB of the pressure reducing valve (6), and a valve is arranged on the oil circuit pipeline.
6. The poppet pump swing valve main control oil passage system of claim 1 wherein, The oil circuit pipeline of the filling pump swing valve main control oil circuit system is further connected with a pressure gauge (9), an accumulator (10), a direct-acting overflow valve (11) and a manual pressure relief valve (12).