CN202047957U - Hydraulic two-cylinder single-acting reciprocating pump driving system adopting turning valve to change direction - Google Patents
Hydraulic two-cylinder single-acting reciprocating pump driving system adopting turning valve to change direction Download PDFInfo
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- CN202047957U CN202047957U CN2011200559633U CN201120055963U CN202047957U CN 202047957 U CN202047957 U CN 202047957U CN 2011200559633 U CN2011200559633 U CN 2011200559633U CN 201120055963 U CN201120055963 U CN 201120055963U CN 202047957 U CN202047957 U CN 202047957U
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- pump
- rotary valve
- reciprocating pump
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Abstract
The utility model aims at providing a hydraulic two-cylinder single-acting reciprocating pump driving system adopting a turning valve to change the direction, which adopts a reversing mechanism combining the turning valve with a reversing vale. The reciprocating pump driving system adopting two pumps to drive a power end so as to further drive a hydraulic end to work, which solves the pressure fluctuation problem of the hydraulic-type reciprocating pump when the direction is changed, and ensures the precise controllability of the reversing process. The hydraulic two-cylinder single-acting reciprocating pump driving system consists of a turning valve, a reversing valve, oil cylinders, a traveling switch, a main pump and an auxiliary pump. The two oil cylinders are respectively connected with the hydraulic end of the reciprocating pump, when a piston in the oil cylinder makes reciprocating movement, the piston in a hydraulic work cylinder is driven to make reciprocating movement, and conveyed medium is absorbed from an intake port and is discharged from a discharging port. The working stroke of the oil cylinder is that oil is supplied by the main pump through the turning valve, and the returning stroke of the oil cylinder is that oil is supplied by the auxiliary pump through the reversing valve. Through the effect of the turning valve, the pulp yield of the two working cylinders are alternatively and gradually reduced and increased, but the pulp yield of the entire pump is constant. The constant pulp yield of the pump can be realized during the transformation process of the working cylinders.
Description
Technical field
Present technique belongs to the engineering construction mechanical field, especially belongs to extraordinary industrial pump, is used to carry elevated pressures and requires discharge flow rate and the fluctuation of pressure try one's best little medium or occasion.As be applied in the oilfield perfusion polymer displacement of reservoir oil technology, and be applied in the hydroelectric project dam foundation grout injection etc., for the occasion of using general reciprocating pump, adopt present technique, also mitigation system vibration greatly improves the equipment operation stationarity.
Background technique
Reciprocating pump is a kind of widely used positive displacement pump, and wherein great majority are with the mechanical type reciprocating pump of connecting rod as power end (drive system), small part is also arranged with the hydraulic type reciprocating pump of hydraulic jack as power end (drive system).The mechanical type reciprocating pump is owing to the inherent characteristic of connecting rod, and the discharge flow rate and the pressure of its fluid end are cyclic fluctuation, and the hydraulic type reciprocating pump generally adopts the selector valve commutation, has sudden change during commutation, and the pressure surge of fluid end is very big.
Summary of the invention
The purpose of this utility model is to provide a kind of changement that adopts rotary valve to combine with general selector valve, double pump drives power end and then drives the reciprocating pump drive system of fluid end work, pressure surge problem when solving the commutation of hydraulic type reciprocating pump, and guarantee that commutation process is accurately controlled.
This system is made up of rotary valve, selector valve, oil cylinder, position limit switch, main pump, auxiliary pump etc.Two oil cylinders are connected with the reciprocating pump fluid end by piston rod respectively, when the piston left and right sides to-and-fro motion in the oil cylinder, drive the reciprocating motion of the pistons in the fluid end clutch release slave cylinder, and the medium of being carried sucks from suction port, discharges from exhaust port.The task of drive system is to require in accordance with regulations to provide power to the fluid end of pump.The working stroke of oil cylinder by main pump by the rotary valve fuel feeding, the backhaul of oil cylinder by auxiliary pump by selector valve and selector valve fuel feeding.By the effect of rotary valve, make the slurry-outlet quantity of two clutch release slave cylinders alternately reduce gradually and increase gradually, and the slurry-outlet quantity of entire pump does not change.Realized that the pump slurry-outlet quantity is constant in the clutch release slave cylinder transfer process.
What use advantage that the design realizes is that pressure surge problem when solving the commutation of hydraulic type reciprocating pump guarantees that commutation process is accurately controlled, has realized that the pump slurry-outlet quantity is constant in the clutch release slave cylinder transfer process.
Description of drawings
Fig. 1 is the reciprocating pump hydraulic scheme;
Fig. 2 is the rotary valve mechanism map.
Among the figure: 1. oil cylinder, 2. piston, 3. oil cylinder, 4. position limit switch, 5. collision block, 6. piston rod, 7. rotary valve, 8. fluid end, 9. clutch release slave cylinder, 10. collision block, 11. Pilot operated check valves, 12. selector valves, 13. selector valves, 14. main pumps, 15. auxiliary pumps;
71. valve body, 72. Returnning springs, 73. contact swing arms, 74. driving discs, 75. valve cores, 76. free wheel devicees, 77. driven discs.
Embodiment
Embodiment below in conjunction with this system of description of drawings.
Fig. 1 is the reciprocating pump hydraulic scheme.This system is made up of rotary valve 7, selector valve 13, oil cylinder 1, oil cylinder 3, position limit switch 4, main pump 14, auxiliary pump 15 etc.Oil cylinder 1, oil cylinder 3 are connected with reciprocating pump fluid end 8 (the dot and dash line frame plays part among the figure) by piston rod respectively, when 2 left and right sides to-and-fro motion of the piston in the oil cylinder, reciprocating motion of the pistons in the clutch release slave cylinder 9 of drive fluid end 8, the medium of being carried sucks from suction port, discharges from exhaust port.The task of drive system is to require in accordance with regulations to provide power to the fluid end of pump.
By rotary valve 7 fuel feeding, the backhaul of oil cylinder 1, oil cylinder 3 (stroke that piston 2 is moved to the left) is passed through selector valve 12 and selector valve 13 fuel feeding by auxiliary pump 15 to the working stroke of oil cylinder 1, oil cylinder 3 (stroke that piston 2 moves right) by main pump 14.The discharge capacity of auxiliary pump 15 is greater than the discharge capacity of main pump 14.Piston rod 6 parallel axes of two oil cylinders are arranged, the axis normal of rotary valve 7 is in piston rod 6 axis, two contacts on the rotary valve 7 correspond respectively to collision block 5 and collision block 10, assurance collision block 5 and collision block 10 can be run into rotary valve 7 contacts respectively, can limit the limit position of oil cylinder stroke in the both sides of collision block 5 or collision block 10, position limit switch 4 is installed.That is, position limit switch 4 has four, is arranged at the working stroke of two piston rods and the limit position of backhaul respectively, and piston rod 6 is provided with the collision block 5,10 that cooperates with position limit switch 4.In the oil cylinder working stroke, when collision block 5 moves the 7 contact swing arms 73 of contact rotary valve, the valve core of rotary valve 7 begins to rotate, when collision block 5 moves to extreme right position, when promptly running into corresponding position limit switch 4 contacts, the valve core 75 of rotary valve 7 stops operating, and when collision block 5 or collision block 10 rotated rotary valve 7 valve cores 75, the sense of rotation of rotary valve 7 valve cores 75 was identical.
Figure two is rotary valve mechanism maps.Valve core 75 is enclosed within the valve body 71 and can rotates in valve body 71, unidirectional mechanism free wheel device 76 is installed at valve core 75 two ends, free wheel device driven disc 77 is connected with valve core 75, driving disc 74 is connected with contact swing arm 73,72, two free wheel devicees 76 of Returnning spring are housed in the contact swing arm 73 can and can only rotate valve core 75 towards a direction around the rotational of valve core 75.When making swing arm 73, external force rotates, be that collision block is when running into contact swing arm 73, contact swing arm 73 drives driving disc 74 and then drive driven disc 77 and valve core 75 and turns over a certain angle, when collision block leaves contact swing arm 73, driving disc 74 resets under the effect of Returnning spring 72, and driven disc 77 and valve core 75 keep motionless.
System works principle: after the system start-up, pipeline is connected in selector valve 13 (or selector valve 12) action, auxiliary pump 15 is to the rod chamber fuel feeding of oil cylinder 3, the collision block 5 of oil cylinder 3 moves to left fast, reach the limit of the position when running into position limit switch 4 contacts, send electrical signal, make 13 times metas of selector valve, auxiliary pump 15 off-loads, simultaneously, main pump 14 is by the rodless cavity fuel feeding of rotary valve 7 to oil cylinder 1, the Pilot operated check valve pressurized is opened, oil cylinder 1 rod chamber oil return, and this moment, the inside hydraulic fluid port of rotary valve 7 only connected one the tunnel, the collision block 10 of oil cylinder 1 moves right, and the fluid end slurry-outlet quantity of entire pump is constant.When collision block 10 is run into rotary valve 7 contacts, rotary valve 7 valve cores begin to rotate, the corner of valve core moves and strengthens along with collision block 10, make the inside hydraulic fluid port of rotary valve 7 connect two-way, it is the rodless cavity oil-feed simultaneously of oil cylinder 1 and oil cylinder 3, the size of two oil cylinder oil inlet quantities changes with moving of collision block 10, the fltting speed of oil cylinder 1 piston is reduced gradually, the fltting speed of oil cylinder 3 pistons improves gradually, being reflected to fluid end is exactly two clutch release slave cylinders pulps simultaneously, and one of them slurry-outlet quantity reduces gradually, and another slurry-outlet quantity increases gradually, and the slurry-outlet quantity of entire pump does not change, and has realized that the pump slurry-outlet quantity is constant in the clutch release slave cylinder transfer process.When collision block 10 arrives extreme right position, the inside hydraulic fluid port of rotary valve 7 is only connected oil cylinder 3 one tunnel, and oil cylinder 3 working strokes are proceeded, and the inside hydraulic fluid port and the oil cylinder 1 of rotary valve 7 are obstructed, simultaneously, collision block 10 is run into corresponding position limit switch 4 contacts, sends electrical signal, makes selector valve 13 move to right and closes, selector valve 12 connection that moves to left, auxiliary pump 15 makes oil cylinder 1 move to left backhaul fast to limit position to oil cylinder 1 rod chamber fuel feeding, waits for that next working stroke arrives.
Claims (5)
1. the hydraulic pressure two cylinder single-acting reciprocating pump drive systems of rotary valve commutation, it is characterized in that: this system comprises rotary valve (7), selector valve (12,13), oil cylinder (1,3), position limit switch (4), main pump (14), auxiliary pump (15); Two oil cylinders pass through separately respectively, and piston rod (6) is connected with the reciprocating pump fluid end; By rotary valve (7) fuel feeding, the backhaul of oil cylinder (1,3) is passed through two selector valves (12,13) fuel feeding by auxiliary pump (15) to the working stroke of oil cylinder (1,3) by main pump (14).
2. hydraulic pressure two cylinder single-acting reciprocating pump drive systems as the commutation of the said rotary valve of claim 1, it is characterized in that: the discharge capacity of auxiliary pump (15) is greater than the discharge capacity of main pump (14).
3. hydraulic pressure two cylinder single-acting reciprocating pump drive systems as the commutation of the said rotary valve of claim 1, it is characterized in that: said position limit switch (4) has four, be arranged at the working stroke of two piston rods (6) and the limit position of backhaul respectively, piston rod (6) is provided with the collision block (5,10) that cooperates with position limit switch (4).
4. hydraulic pressure two cylinder single-acting reciprocating pump drive systems as the commutation of the said rotary valve of claim 1, it is characterized in that: piston rod (6) parallel axes that it is characterized in that said two oil cylinders is arranged, the axis normal of rotary valve (7) is in piston rod (6) axis, two contacts that have on the rotary valve (7) correspond respectively to collision block (5) and collision block (10), and collision block (5) and collision block (10) can be run into the contact of rotary valve (7) respectively.
5. hydraulic pressure two cylinder single-acting reciprocating pump drive systems as claim 1 or the commutation of 4 said rotary valves, it is characterized in that: said rotary valve (7), be enclosed within the valve body (71) and can in valve body (71), rotate by valve core (75), unidirectional mechanism free wheel device (76) is installed at valve core (75) two ends, free wheel device driven disc (77) is connected with valve core (75), driving disc (74) is connected with contact swing arm (73), Returnning spring (72) is housed in the contact swing arm (73), and two free wheel devicees (76) can and can only rotate valve core (75) towards a direction around the rotational of valve core (75).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200559633U CN202047957U (en) | 2011-03-02 | 2011-03-02 | Hydraulic two-cylinder single-acting reciprocating pump driving system adopting turning valve to change direction |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200559633U CN202047957U (en) | 2011-03-02 | 2011-03-02 | Hydraulic two-cylinder single-acting reciprocating pump driving system adopting turning valve to change direction |
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| Publication Number | Publication Date |
|---|---|
| CN202047957U true CN202047957U (en) | 2011-11-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011200559633U Expired - Lifetime CN202047957U (en) | 2011-03-02 | 2011-03-02 | Hydraulic two-cylinder single-acting reciprocating pump driving system adopting turning valve to change direction |
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| CN (1) | CN202047957U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102135080A (en) * | 2011-03-02 | 2011-07-27 | 浙江杭钻机械制造股份有限公司 | Hydraulic double-cylinder single-acting reciprocating pump driving system capable of reversing by rotary valve |
| CN104653424A (en) * | 2015-03-09 | 2015-05-27 | 镇江长城注浆设备有限公司 | Spring-boosted triggering delay reversing pneumatic grouting pump |
| CN109667801A (en) * | 2018-12-10 | 2019-04-23 | 浙江杭钻能源装备有限公司 | The slip casting pump hydraulic system of constant current can be met |
-
2011
- 2011-03-02 CN CN2011200559633U patent/CN202047957U/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102135080A (en) * | 2011-03-02 | 2011-07-27 | 浙江杭钻机械制造股份有限公司 | Hydraulic double-cylinder single-acting reciprocating pump driving system capable of reversing by rotary valve |
| CN104653424A (en) * | 2015-03-09 | 2015-05-27 | 镇江长城注浆设备有限公司 | Spring-boosted triggering delay reversing pneumatic grouting pump |
| CN104653424B (en) * | 2015-03-09 | 2016-08-17 | 镇江长城注浆设备有限公司 | Spring assist Time delay commutation Pneumatic grouting pump |
| CN109667801A (en) * | 2018-12-10 | 2019-04-23 | 浙江杭钻能源装备有限公司 | The slip casting pump hydraulic system of constant current can be met |
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| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20111123 |