CN201461362U - Variable control mechanism of plunger piston variable pump - Google Patents
Variable control mechanism of plunger piston variable pump Download PDFInfo
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- CN201461362U CN201461362U CN2009200738640U CN200920073864U CN201461362U CN 201461362 U CN201461362 U CN 201461362U CN 2009200738640 U CN2009200738640 U CN 2009200738640U CN 200920073864 U CN200920073864 U CN 200920073864U CN 201461362 U CN201461362 U CN 201461362U
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Abstract
The utility model discloses a variable control mechanism of a plunger piston variable pump, comprising the plunger piston variable pump which is provided with a left variable oil cylinder component and a right variable oil cylinder component that are used for outputting oil supplied by the load of a hydraulic system into a main oil channel and adjusting the dip angle change of a swash plate; furthermore, the variable control mechanism also comprises a constant power valve, a pressure shut-off valve and a load sensitive valve. By adopting the constant power valve, the pressure shut-off valve and the load sensitive valve, the variable control mechanism realizes three control functions of constant power, pressure shut-off and sensitive load at the same time; in addition, the variable control mechanism not only has simple structure, but also greatly improves the work stability of the plunger piston variable pump and has the advantage of energy conservation.
Description
Technical field
The utility model belongs to the oil hydraulic pump technical field, relates to plunger variable pump, relates in particular to the Variable Control mechanism of plunger variable pump.
Background technique
Along with the development of technology, hydraulic system is increasing to the demand of variable displacement pump, and is also more and more higher to the variable format requirement of oil hydraulic pump.The Variable Control mode of the plunger variable pump that occurs both at home and abroad is mainly based on single variable format of planting now, for example constant-pressure variable control, permanent power and variable control etc., these Variable Control modes generally can only realize a kind of variable function, function singleness can not satisfy the many-sided performance requirement of hydraulic system (as satisfying functions such as power adjustments, energy-conservation, overflow simultaneously).Want to realize multi-functional can only achieving the goal, so just cause system bulk to increase, install inconvenient by the mode that control oil channel is set.Even existing variable control system itself also is that volume is bigger, efficient is low, less stable.
The model utility content
Technical problem to be solved in the utility model provides a kind of Variable Control mechanism of plunger variable pump, this system can realize permanent power, pressure cut off and three functions of load-sensitive control simultaneously, thereby reach energy-conservation purpose, improve the working stability of plunger variable pump.
In order to solve the problems of the technologies described above, the utility model adopts following technological scheme:
A kind of Variable Control mechanism of plunger variable pump, comprise plunger variable pump, described plunger variable pump has for the load fuel feeding output working connection of hydraulic system and is used for regulating left variable cylinder component and the right variable cylinder component that swashplate angle changes, and it is characterized in that: also include constant power valve, pressure shut-off valve and load-sensitive valve;
Have actuator port and positioning pressure hydraulic fluid port on the described output working connection, actuator port is communicated to the oil cylinder in the right variable cylinder component;
Described constant power valve has mechanical spool diverter switch, the 1st valve port, the 2nd valve port and the 3rd valve port, described pressure shut-off valve has pressure valve core diverter switch, the 1st valve port, the 2nd valve port and the 3rd valve port, and described load-sensitive valve has pressure ratio than spool diverter switch, the 1st valve port, the 2nd valve port and the 3rd valve port;
Connect by connecting rod between the variable piston rod in the described right variable cylinder component and the mechanical spool diverter switch of constant power valve, the 1st valve port of described constant power valve, pressure shut-off valve and load-sensitive valve and the pressure valve core diverter switch of pressure shut-off valve all are communicated with the pressure end connection output working connection of the pressure ratio of positioning pressure hydraulic fluid port and load-sensitive valve than the spool diverter switch, and another pressure end is communicated with the load flow vent line of output working connection after load;
The 2nd valve port of described constant power valve is communicated with fuel tank, and the 3rd valve port is communicated with the 2nd valve port of pressure shut-off valve, and pressure shut-off valve the 3rd valve port is communicated with the 2nd valve port of load-sensitive valve, and the 3rd valve port of load-sensitive valve is communicated with the oil cylinder in the left cylinder component.
Adopt technique scheme, the Variable Control mechanism of plunger variable pump of the present utility model has realized permanent power, pressure cut off and three control functions of load-sensitive simultaneously by adopting constant power valve, pressure shut-off valve and load-sensitive valve, not only simple in structure, and can make the working stability of plunger variable pump improve greatly and have energy-conservation advantage.
Description of drawings
Below in conjunction with the drawings and specific embodiments the utility model is elaborated:
Fig. 1 is a system construction drawing of the present utility model.
Embodiment
As shown in Figure 1, the Variable Control mechanism of plunger variable pump of the present utility model comprises plunger variable pump 100, constant power valve 200, pressure shut-off valve 300 and load-sensitive valve 400.
Wherein, plunger variable pump 100 filler openings from inlet port S inspiration hydraulic oil, and be load 003 fuel feeding the hydraulic system from oil outlet through output working connection 001 through input working connection 002, and exporting working connection 001 is load flow vent line 004 after load 003.
In plunger variable pump 100, have and regulate swash plate 101 inclination angles with the left cylinder component 110 of change plunger variable pump 100 output powers with by cylinder component 120.Wherein, variable piston 112 during left side cylinder component 110 has oil cylinder 111 and is located at oil cylinder 111 and an end link variable piston 112, the other end are connected the adjustable lever 113 of swash plate 101 left ends, have returning spring 114 between variable piston 112 bottoms and oil cylinder 111 bottoms.The adjustable lever 123 that the variable piston rod 122 during right cylinder component 120 has oil cylinder 121 and is located at oil cylinder 121 and an end link variable piston rod 122 the other ends are connected swash plate 101 right-hand members also is provided with returning spring 124 between variable piston rod 122 and oil cylinder 121.
Have actuator port A and positioning pressure hydraulic fluid port G on the output working connection 001, actuator port A is communicated to the oil cylinder 121 in the right variable cylinder component 120.
Connect 500 by connecting rod between the variable piston rod 122 in the right variable cylinder component 120 and the mechanical spool diverter switch K1 of constant power valve 200, the pressure valve core diverter switch K2 of the 1st valve port of constant power valve 200, pressure shut-off valve 300 and load-sensitive valve 400 and pressure shut-off valve 300 all is communicated with the pressure end P1 connection output working connection 001 of the pressure ratio of positioning pressure hydraulic fluid port G and load-sensitive valve 400 than spool diverter switch K3, and another pressure end P2 is communicated with load flow vent line 004.
The 2nd valve port of constant power valve 200 is communicated with fuel tank 005, the 3rd valve port is communicated with the 2nd valve port of pressure shut-off valve 300, pressure shut-off valve 300 the 3rd valve port is communicated with the 2nd valve port of load-sensitive valve 400, and the 3rd valve port of load-sensitive valve 400 is communicated with the oil cylinder 111 in the left cylinder component 110.
In order to reduce boundary dimension, constant power valve 200 of the present utility model, pressure shut-off valve 300 and load-sensitive valve 400 are integrated on the valve piece.
In addition, between the oil cylinder 121 of actuator port A and right cylinder component 120, be provided with throttle valve 600, between the 3rd valve port of load-sensitive valve 400 and the oil cylinder 111 in the left cylinder component 110, also be provided with throttle valve 600.The effect of throttle valve 600 is flows of the variable pipeline of control oil hydraulic pump, the variable speed of regulator solution press pump, the running of stable liquid pump.
It more than is exactly the Variable Control mechanism of plunger variable pump of the present utility model, when the power of plunger variable pump 100 output just in time the time, promptly Shu Chu oil mass just in time, the oil pressure of output in the working connection 001 is just in time the time, output working connection 001 flows to oil pressure the oil cylinder 121 from actuator port A and can't promote variable piston rod 122 and move, also just can't touch the mechanical spool diverter switch K1 of constant power valve 200 by connecting rod 500, at this moment, the 2nd valve port of constant power valve 200 and the 3rd valve port are communicated with, at this moment because output working connection 001 pressure ratio is lower, do not reach the pressure set points of pressure shut-off valve 300, the 2nd valve port and the 3rd valve port of pressure shut-off valve 3 also are communicated with, if load (performance of oil pressure in oil circuit export oil pressure in the working connection 001 and load flow vent line 004 oil pressure also suitable) also working properly, at this moment, the 2nd valve port and the 3rd valve port of load-sensitive valve 400 also are communicated with, and just do not have hydraulic oil can be input to oil cylinder 111 in the left cylinder component 110, and swash plate 101 just keeps the inclination angle stably to work so.
If oil pressure is too high in the output working connection 001, but there is not yet proper functioning of the pressure set points of Overpressure of a safety valve cut-off valve 3 and load, the hydraulic oil of high pressure will promote variable piston rods 122 from the oil cylinder 121 that actuator port A enters right cylinder component 120 and move, and by touch the mechanical spool diverter switch K1 of constant power valve 200 by connecting rod 500, the 2nd valve port and the 3rd valve port of constant power valve 200 are cut off, the 1st valve port and the 3rd valve port are communicated with, the high pressure oil that enters from positioning pressure mouth G is through the 1st valve port of constant power valve 200, the 3rd valve port, the 2nd valve port of pressure shut-off valve 3, the 3rd valve port, thereby the 2nd valve port of load-sensitive valve 400 and the 3rd valve port enter the oil cylinder 111 of left cylinder component 110 and promote to move on the variable piston 112, and then promoting the left end rising of swash plate 101 through adjustable lever 113 to reduce the inclination angle of swash plate 101, thereby reduce the output power of plunger variable pump, make the steady state of the output power answer of plunger variable pump.
If oil pressure is low excessively in the output working connection 001, under returning spring 114 effects of the returning spring 124 of right cylinder component 120 and left cylinder component 110, the inclination angle of swash plate 101 can increase automatically, thereby improves output power.
In case if the dangerous high oil pressure of the pressure set points of plunger variable pump unexpected output of moment Overpressure of a safety valve cut-off valve 3; at this moment export the pressure valve core diverter switch K2 that dangerous high oil pressure in the working connection 001 can touch pressure shut-off valve 300; the 2nd valve port and the 3rd valve port of pressure shut-off valve 300 are cut off; the 1st valve port and the 3rd valve port are communicated with; at this moment the dangerous high pressure oil that flows to from positioning pressure mouth G is just through the 1st valve port of pressure shut-off valve 300; the 3rd valve port; thereby the 2nd valve port of load-sensitive valve 400 and the 3rd valve port enter the oil cylinder 111 of left cylinder component 110 rapidly and promote variable pistons 112 and move on to the end on fast; and then make adjustable lever 113 promote swash plate 101 fast with the inclination angle vanishing, plunger variable pump is quit work rapidly to play the effect of protective system.
When load 003 is broken down; at this moment the oil pressure of exporting in the working connection 001 can be apparently higher than the oil pressure in the load flow vent line 004; the pressure end P1 that is the comparison spool diverter switch K3 of load-sensitive valve 400 senses the oil pressure that oil pressure can obviously sense greater than pressure end P2; at this moment the comparison spool diverter switch K3 of load-sensitive valve 400 makes the 2nd valve port of load-sensitive valve 400 and the 3rd valve port cut off; the 1st valve port and the 3rd valve port are communicated with; thereby from flow to 1st valve port of high pressure oil from positioning pressure mouth G through load-sensitive valve 400; thereby the 3rd valve port enters the oil cylinder 111 of left cylinder component 110 and promotes variable pistons 112 and move on to the end on fast; and then make adjustable lever 113 promote swash plate 101 fast with the inclination angle vanishing; plunger variable pump is quit work rapidly to play the effect of protective system; and also avoided the meaningless work of oil hydraulic pump, saved energy.
More than be exactly the Variable Control mechanism and the working procedure thereof of plunger variable pump of the present utility model, by describing in detail, as can be seen, the utility model is by being carried in three kinds of Variable Control (permanent power, pressure cut off, load-sensitive) mode on the pump, realize multiple kind of variable format by an integrated valve block and built-in variable actuator, have following advantage:
1, three kinds of valves link mutually, can realize parameters such as power, pressure, flow are controlled, and satisfy the multiple demand of hydraulic system, as power adjustments, energy-conservation, protective system safety etc.
2, Variable Control good stability;
3, volume is little, the level of integration height.
But, one skilled in the art would recognize that above-mentioned embodiment is exemplary, be to be the restriction that this patent is comprised scope in order better to make those skilled in the art can understand this patent, can not to be interpreted as; So long as according to spirit that this patent discloses done anyly be equal to change or modify, all fall into the scope that this patent comprises.
Claims (3)
1. the Variable Control mechanism of a plunger variable pump, comprise plunger variable pump, described plunger variable pump has for the load fuel feeding output working connection of hydraulic system and is used for regulating left variable cylinder component and the right variable cylinder component that swashplate angle changes, and it is characterized in that: also include constant power valve, pressure shut-off valve and load-sensitive valve;
Have actuator port and positioning pressure hydraulic fluid port on the described output working connection, actuator port is communicated to the oil cylinder in the right variable cylinder component;
Described constant power valve has mechanical spool diverter switch, the 1st valve port, the 2nd valve port and the 3rd valve port, described pressure shut-off valve has pressure valve core diverter switch, the 1st valve port, the 2nd valve port and the 3rd valve port, and described load-sensitive valve has pressure ratio than spool diverter switch, the 1st valve port, the 2nd valve port and the 3rd valve port;
Connect by connecting rod between the variable piston rod in the described right variable cylinder component and the mechanical spool diverter switch of constant power valve, the 1st valve port of described constant power valve, pressure shut-off valve and load-sensitive valve and the pressure valve core diverter switch of pressure shut-off valve all are communicated with the pressure end connection output working connection of the pressure ratio of positioning pressure hydraulic fluid port and load-sensitive valve than the spool diverter switch, and another pressure end is communicated with the load flow vent line of output working connection after load;
The 2nd valve port of described constant power valve is communicated with fuel tank, and the 3rd valve port is communicated with the 2nd valve port of pressure shut-off valve, and pressure shut-off valve the 3rd valve port is communicated with the 2nd valve port of load-sensitive valve, and the 3rd valve port of load-sensitive valve is communicated with the oil cylinder in the left cylinder component.
2. the Variable Control mechanism of plunger variable pump according to claim 1, it is characterized in that: described constant power valve, pressure shut-off valve and load-sensitive valve are integrated on the valve piece.
3. the Variable Control mechanism of plunger variable pump according to claim 1, it is characterized in that: be provided with throttle valve between the oil cylinder of described actuator port and right cylinder component, also be provided with throttle valve between the 3rd valve port of described load-sensitive valve and the oil cylinder in the left cylinder component.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200738640U CN201461362U (en) | 2009-05-05 | 2009-05-05 | Variable control mechanism of plunger piston variable pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200738640U CN201461362U (en) | 2009-05-05 | 2009-05-05 | Variable control mechanism of plunger piston variable pump |
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| CN201461362U true CN201461362U (en) | 2010-05-12 |
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| CN2009200738640U Expired - Fee Related CN201461362U (en) | 2009-05-05 | 2009-05-05 | Variable control mechanism of plunger piston variable pump |
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| CN (1) | CN201461362U (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101922445A (en) * | 2010-07-29 | 2010-12-22 | 杭州力龙液压有限公司 | Constant power control valve |
| CN102330667A (en) * | 2011-10-10 | 2012-01-25 | 安徽博一流体传动股份有限公司 | Plunger pump with self-controlled type cross total power control and variable power |
| CN102556153A (en) * | 2011-12-31 | 2012-07-11 | 上海电气液压气动有限公司 | Steering hydraulic drive system for vehicle |
| CN102828942A (en) * | 2011-06-16 | 2012-12-19 | 中联重科股份有限公司 | Constant-power control device and method for variable displacement pump and concrete pumping installation |
| CN104234118A (en) * | 2013-12-13 | 2014-12-24 | 江苏恒立液压有限公司 | Pump for compact excavator |
| CN104533774A (en) * | 2014-12-03 | 2015-04-22 | 安徽博一流体传动股份有限公司 | Variable displacement piston pump for loading machine |
| CN104728193A (en) * | 2015-03-18 | 2015-06-24 | 北京航空航天大学 | Load-sensitive electro-hydrostatic actuator |
| CN106089868A (en) * | 2016-08-09 | 2016-11-09 | 徐州重型机械有限公司 | Energy recovery pump, road vehicle and engineering machinery |
| CN107906064A (en) * | 2017-12-25 | 2018-04-13 | 邵阳维克液压股份有限公司 | The device and variable method for control speed of changeable constant pressure variable displacement pump variable speed |
-
2009
- 2009-05-05 CN CN2009200738640U patent/CN201461362U/en not_active Expired - Fee Related
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101922445B (en) * | 2010-07-29 | 2013-08-21 | 杭州力龙液压有限公司 | Constant power control valve |
| CN101922445A (en) * | 2010-07-29 | 2010-12-22 | 杭州力龙液压有限公司 | Constant power control valve |
| CN102828942B (en) * | 2011-06-16 | 2015-11-18 | 中联重科股份有限公司 | The constant power control device of variable displacement pump, method and the concrete pump set |
| CN102828942A (en) * | 2011-06-16 | 2012-12-19 | 中联重科股份有限公司 | Constant-power control device and method for variable displacement pump and concrete pumping installation |
| CN102330667B (en) * | 2011-10-10 | 2014-09-10 | 安徽博一流体传动股份有限公司 | Plunger pump with self-controlled type cross total power control and variable power |
| CN102330667A (en) * | 2011-10-10 | 2012-01-25 | 安徽博一流体传动股份有限公司 | Plunger pump with self-controlled type cross total power control and variable power |
| CN102556153A (en) * | 2011-12-31 | 2012-07-11 | 上海电气液压气动有限公司 | Steering hydraulic drive system for vehicle |
| CN104234118A (en) * | 2013-12-13 | 2014-12-24 | 江苏恒立液压有限公司 | Pump for compact excavator |
| CN104234118B (en) * | 2013-12-13 | 2017-01-04 | 江苏恒立液压科技有限公司 | Mini-excavator pump |
| CN104533774A (en) * | 2014-12-03 | 2015-04-22 | 安徽博一流体传动股份有限公司 | Variable displacement piston pump for loading machine |
| CN104728193A (en) * | 2015-03-18 | 2015-06-24 | 北京航空航天大学 | Load-sensitive electro-hydrostatic actuator |
| CN104728193B (en) * | 2015-03-18 | 2017-03-08 | 北京航空航天大学 | The Electrical hydrostatic actuator of load-sensitive |
| CN106089868A (en) * | 2016-08-09 | 2016-11-09 | 徐州重型机械有限公司 | Energy recovery pump, road vehicle and engineering machinery |
| CN106089868B (en) * | 2016-08-09 | 2018-05-18 | 徐州重型机械有限公司 | energy recovery pump, road vehicle and engineering machinery |
| CN107906064A (en) * | 2017-12-25 | 2018-04-13 | 邵阳维克液压股份有限公司 | The device and variable method for control speed of changeable constant pressure variable displacement pump variable speed |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| ASS | Succession or assignment of patent right |
Owner name: SAUER-DANFOSS-DAIKIN MOBILE HYDRAULICS (SHANGHAI) Free format text: FORMER OWNER: SHANGHAI ELECTRIC HYDRAULIC + PNEUMATICS CO., LTD. Effective date: 20100920 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| COR | Change of bibliographic data |
Free format text: CORRECT: ADDRESS; FROM: 200237 NO.2188, XINZHU ROAD, MINHANG DISTRICT, SHANGHAI TO: 201200 NO.626, RONGQIAO ROAD, PUDONG NEW DISTRICT, SHANGHAI |
|
| TR01 | Transfer of patent right |
Effective date of registration: 20100920 Address after: 201200, banyan Road, 626, Shanghai, Pudong New Area Patentee after: Shanghai Sa'ao Hydraulic Driving Co., Ltd. Address before: 200237 Shanghai Minhang District Xin Zhu Road No. 2188 Patentee before: Shanghai Electric Hydraulics and Pneumatics Co., Ltd. |
|
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100512 Termination date: 20150505 |
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| EXPY | Termination of patent right or utility model |