CN103174816B - A kind of pressure differential control type stepless speed variator flow active control system - Google Patents
A kind of pressure differential control type stepless speed variator flow active control system Download PDFInfo
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- CN103174816B CN103174816B CN201310113576.4A CN201310113576A CN103174816B CN 103174816 B CN103174816 B CN 103174816B CN 201310113576 A CN201310113576 A CN 201310113576A CN 103174816 B CN103174816 B CN 103174816B
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Abstract
The invention discloses a kind of pressure differential control type stepless speed variator flow active control system, comprise a duplex oil hydraulic pump, duplex oil hydraulic pump is divided into main pump unit and auxiliary pump unit, and main pump unit is connected with fuel tank with the filler opening of auxiliary pump unit, and the rotor of duplex oil hydraulic pump is connected with oil hydraulic pump; The oil outlet of main pump unit connects main one-way valve and secondary one-way valve respectively, and the other end of main one-way valve connects filler opening and the restriction of relief valve respectively, the oil outlet connected tank of relief valve; Another termination actuator of restriction; The A mouth of another termination selector valve of secondary one-way valve; The oil outlet of auxiliary pump unit connects the A mouth of selector valve; The O mouth connected tank of selector valve, C mouth meet restriction, A Kou Jie actuator.The invention has the beneficial effects as follows: the energy loss that hydraulic system 1, can be reduced; 2, the service behaviour reaching in real time flow switch is accurately easy to; 3, significantly system works efficiency is improved; 4, system architecture is simple, and user cost is low.
Description
Technical field
The present invention relates to a kind of pressure differential control type stepless speed variator flow active control system, be mainly used in stepless speed variator hydraulic system, especially the stepless speed variator hydraulic system of small volume, low cost.
Background technique
At present along with energy crisis situation is increasingly serious; the energy shortage problem faced is day by day serious; changing the common theme of arising at the historic moment in spring tide in world today's development is energy-saving and emission-reduction, and people-oriented, and the development in automatic gearbox field also should comply with this trend and trend.Since the eighties in last century, automatic gearbox using efficient, energy-conservation, operate comfortable, safe, reliable as mainly pursuing a goal; Enter the nineties in 20th century, motor-dom is to the research and development pay attention to day by day of stepless speed variator technology, employing energy-saving pump designs, the requirement of better adaptation Under Different Work Condition of Engine, carry out the Flow-rate adjustment of system according to the different working condition requirements of motor, by Flow-rate adjustment and flow switch, reduce unnecessary flow loss and energy loss, improve the efficiency of whole stepless speed variator, thus reach the object of energy-saving and emission-reduction.According to current technology future developing trend, each parts of stepless speed variator all will realize customizations, the flow switch system that stepless speed variator is special so in the future also will be applied, and therefore the developmental research of the flow switch systems technology that stepless speed variator is special just seems especially necessary and important.
Oil hydraulic pump oil supply system is a very important part inside stepless speed variator technique system, is the critical component of whole system.It is little that double-action blade structure has size, lightweight, uniform flow and the advantage such as noise is low, be widely used in all kinds of small-sized hydraulic system, existing hydraulic system is that employing double-acting vane pump carries out single oil pump feed, double-acting vane pump generally brings driving by motor by transmission, therefore the output flow of double-acting vane pump is directly proportional to engine speed, the flow that when operating to prevent high engine speeds, oil hydraulic pump exports is excessive, adverse effect is caused to the safety of actuator, general in systems in which by relief valve and throttle valve composition current limiting pressure-limiting valve group, overflow the excess traffic part exceeding peak rate of flow oil sump tank.Find by analyzing, existing hydraulic system comes with some shortcomings: single-pump system flow can not regulate, can only be overflow back by valve group and exceed the excess traffic part of peak rate of flow, so just create a large amount of energy losses, reduce the working efficiency of whole system, thus also reducing the transmission efficiency of stepless speed variator, excess traffic is more, and power loss is larger.Experimentally data analysis, in the energy loss of this hydraulic system, V belt translation energy loss, the energy loss of system weight, the energy loss of oil hydraulic pump accounts for 17% greatly, and the energy loss of nearly 46% originate this current limiting pressure-limiting valve group produce excess traffic among, finally only be approximately 3% for useful horsepower, so want to reach energy-saving and emission-reduction, the developing goal reduced costs, promote the service behaviour of whole stepless speed variator system, improve the working efficiency of whole stepless speed variator system, improve the technical advantage of stepless speed variator, the energy loss problem existed in resolution system will be puted forth effort, reduce the excessive power loss brought because of " excess traffic ", thus reduction power loss, improve the transmission efficiency of stepless speed variator.
Summary of the invention
The object of the invention is to solve in existing hydraulic system that energy loss is large, power loss is high, the problem such as the low and control efficiency of system works efficiency is low, a kind of pressure differential control type stepless speed variator flow active control system is provided, flow system flow is carried out to the real-time adjustment of pressure differential control type.
Technological scheme of the present invention is, a kind of pressure differential control type stepless speed variator flow active control system, comprise a duplex oil hydraulic pump, duplex oil hydraulic pump is divided into main pump unit and auxiliary pump unit, main pump unit is connected with fuel tank with the filler opening of auxiliary pump unit, and the rotor of duplex oil hydraulic pump is connected with oil hydraulic pump; The oil outlet of main pump unit connects main one-way valve and secondary one-way valve respectively, and the other end of main one-way valve connects filler opening and the restriction of relief valve respectively, the oil outlet connected tank of relief valve; Another termination actuator of restriction; The filler opening A of another termination selector valve of secondary one-way valve; The oil outlet of auxiliary pump unit meets the filler opening A of selector valve; The oil outlet O connected tank of selector valve, the rear end that lower outside control mouth C connects the front end of restriction, upper outside control mouth B connects restriction 5.
The double action vane pump of main pump unit and auxiliary pump unit to be discharge capacity be 8ml/r.
The range of regulation of relief valve is 0 ~ 6MPa.
Restriction is an aperture
metal aperture.
Selector valve is a gradual formula bi-bit bi-pass selector valve, comprises, bonnet, bottom flange, bonnet spring, spool, bottom flange spring, movable valve seat, filler opening A, oil outlet O, upper outside control mouth B, lower outside control mouth C; Bonnet and bottom flange are bolted, and spool has U-groove bevel, have upper end blind hole in spool upper end, have lower end blind hole in spool lower end, and lower end blind hole has damping hole.
The present invention has following technique effect, the present invention installs a gear and engages with the driven gear that another matches on engine output shaft, driven gear axle head installs a duplex pump, this axle drives duplex pump synchronous rotary, output flow is directly proportional to the rotating speed of motor, carries out real-time contacts with engine operating condition; This duplex pump is as Hydraulic power units to system fuel feeding, and hydraulic pump outlet links an one-way valve, prevents oil return.The outlet of auxiliary pump unit is exported with main pump unit and is connected by one-way valve, utilizes one-way valve to carry out the control flowed to, and realizes interflow and shunting; Carry out pressurize by relief valve, the pressure stability of keeping system, system pressure maximum is 5MPa.By restriction two ends pressure reduction is introduced in selector valve, hydraulic coupling and the differential of spring force is utilized to go the commutation of manipulation selector valve, the work being realized auxiliary pump unit by the commutation of selector valve is switched, thus reaches the flow switch of the system of realization, reduces the object of energy loss; The invention has the beneficial effects as follows: the energy loss that hydraulic system 1, can be reduced; 2, the service behaviour reaching in real time flow switch is accurately easy to; 3, significantly system works efficiency is improved; 4, system architecture is simple, and user cost is low.
Accompanying drawing explanation
Fig. 1 is structural principle schematic diagram of the present invention.
Fig. 2 is the structural representation of selector valve of the present invention.
Embodiment
As shown in Figure 1, a kind of pressure differential control type stepless speed variator flow active control system, comprise a duplex oil hydraulic pump 1, duplex oil hydraulic pump 1 is divided into main pump unit 9 and auxiliary pump unit 8, main pump unit 9 is connected with fuel tank 2 with the filler opening of auxiliary pump unit 8, and the rotor of duplex oil hydraulic pump 1 is connected with oil hydraulic pump 3; The oil outlet of main pump unit 9 connects main one-way valve 11 and secondary one-way valve 10 respectively, and the other end of main one-way valve 11 connects filler opening and the restriction 5 of relief valve 4, the oil outlet connected tank 2 of relief valve 4 respectively; Another termination actuator 6 of restriction 5, described actuator 6 is stepless speed variator metal tape fastening device; The filler opening A of another termination selector valve 7 of secondary one-way valve 10; The oil outlet of auxiliary pump unit 8 meets the filler opening A of selector valve 7; The oil outlet O connected tank 2 of selector valve 7, the rear end that lower outside control mouth C connects the front end of restriction 5, upper outside control mouth B connects restriction 5, the double action vane pump of main pump unit 9 and auxiliary pump unit 8 to be discharge capacities be 8ml/r; The range of regulation of relief valve 4 is 0 ~ 6MPa; Restriction 5 is apertures
metal aperture; Selector valve 7 is gradual formula bi-bit bi-pass selector valves.
The present invention utilizes a duplex oil hydraulic pump 1 for system fuel feeding, and engine output shaft is connected with the rotor of duplex oil hydraulic pump 1, and with engine output shaft synchronous axial system, output flow is directly proportional to engine speed, in real time each work condition state of reflection motor; Pair vane pump 1 from fuel tank 2 oil suction, and exports fluid from main pump unit 9 and the respective oil outlet of auxiliary pump unit 8.When the engine speed is lower, the flow of duplex oil hydraulic pump 1 output is also less.Now selector valve 7 is in the state disconnecting oil circuit, and the fluid that auxiliary pump unit 8 exports can only flow to the oil outlet of main pump unit 9 by secondary one-way valve 10, the fluid exported with main pump unit 9 collaborates, and is actuator 6 fuel feeding together.Being worked by actuator 6, to set restriction pressure reduction be 0.1MPa to required flow 25L/min, restriction 5 radius
restriction 5 two ends size pressure signal access selector valve 7.Along with the output flow of the main pump unit 9 and auxiliary pump unit 8 that improve duplex oil hydraulic pump 1 gradually of engine speed also increases gradually.When engine speed is brought up to a certain degree time, the interflow exported by main pump unit 9 and auxiliary pump unit 8 has flowed exceed peak rate of flow, now restriction 5 two ends reach pressure reduction 0.1MPa, the pressure difference signal at restriction 5 two ends is introduced outside control mouth B on selector valve 7, lower outside control mouth C, realizes commutation by hydraulic coupling and spring force Differential Control selector valve 7.Selector valve 7 carries out gradual formula commutation, the fluid that now auxiliary pump unit 8 exports directly flows back to fuel tank by selector valve 7 oil outlet O, due to the gradual commutation of selector valve 7, ensure that flow system flow is stabilized in 25L/min, the pressure gradual change in auxiliary pump unit 8 outlet port drops to zero, secondary one-way valve 10 is closed, and stops the fluid of main pump unit 9 to flow back to the oil outlet of auxiliary pump unit 8.Therefore only have a main pump unit 9 to export fluid to actuator 6 in which final state, the unnecessary fluid thus only having main pump unit 9 to export flows back to fuel tank 2 by relief valve 4 and produces power loss.Auxiliary pump unit 8 is by selector valve 7 oil return, and because the opening amount of selector valve 7 is very large, auxiliary pump unit 8 outlet pressure is close to zero, and therefore acting is approximately zero, thus the power loss produced is minimum, negligible.By said method, decrease the flow loss by relief valve 4 oil return, and then reduce the energy loss that this part excess traffic causes.
As shown in Figure 2, control to realize flow switch, selector valve 7 is gradual formula bi-bit bi-pass selector valves, comprises, bonnet 12, bottom flange 16, bonnet spring 13, spool 14, bottom flange spring 17, movable valve seat 18, filler opening A, oil outlet O, upper outside control mouth B, lower outside control mouth C; Bonnet 12 is connected by bolt 15 with bottom flange 16, spool 14 has U-groove bevel 19, upper end blind hole 20 is had in spool 14 upper end, lower end blind hole 21 is had in spool 14 lower end, lower end blind hole 21 has damping hole 22, and upper outside control mouth B, lower outside control mouth C access the little pressure signal at restriction 5 two ends and large pressure signal respectively; Movable valve seat 18 one end contacts with spool 14, and the other end connects bottom flange spring 17; Spool 14 the other end has bonnet spring 13; When flow system flow does not reach actuator's working flow, by the pressure maintaining effect of relief valve 4, selector valve 7 reaches state of equilibrium by hydraulic coupling and spring force, and now selector valve 7 is blocking state with upper outside control mouth B; When flow system flow reaches the working flow of actuator, now restriction 5 two ends pressure reduction reaches 0.1MPa, introduce the large pressure signal at restriction 5 two ends and little pressure signal respectively, the pressure oil of lower outside control mouth C mouth enters into the lower end blind hole 21 of spool 14 through movable valve seat 18, a part of fluid is flowed out from oil outlet O mouth by damping hole 22; The pressure oil of upper outside control mouth B mouth enters spool 14 upper end blind hole 20, in selector valve 7, now forms hydraulic coupling poor, thus realizes the commutation of selector valve 7; Bonnet spring 13 and bottom flange spring 17 is provided with in selector valve 7, by the alternately accumulation of energy of spring with release and can act on adjustable change valve 7 commutating speed, select the spring compared with large rigidity, thus reach the fluctuation of reduction output flow, reduce the object of hydraulic vibration and impact; Spool 14 has U-type groove 19, when selector valve 7 is not also opened completely, then some enters hydraulic pressure oil duct by U-type groove 19 to the fluid of filler opening A, flow out from oil outlet O, when selector valve 7 is opened completely, then U-type groove 19 is ineffective, and filler opening A and oil outlet O are directly communicated with can reach the whole reversing impact of selector valve 7 of reduction and the fluctuation of output flow, make the stability of system higher, flow switch working efficiency is higher.Selector valve 7 can commutate continuously according to the real-time working condition of motor, real-time pressure and the flow of adjustment auxiliary pump unit 8 export, and then realize flow switch, regulating system uninterrupted, make system ensure that actuator normally works under the prerequisite reducing flow loss and energy loss.Adopt this gradual formula bi-bit bi-pass structure of reversing valve simply compact, be convenient to mounting and adjusting, low cost of manufacture.
Claims (4)
1. a pressure differential control type stepless speed variator flow active control system, comprise a duplex oil hydraulic pump (1), duplex oil hydraulic pump (1) is divided into main pump unit (9) and auxiliary pump unit (8), it is characterized in that: main pump unit (9) is connected with fuel tank (2) with the filler opening of auxiliary pump unit (8), the oil outlet of main pump unit (9) connects main one-way valve (11) and secondary one-way valve (10) respectively, the other end of main one-way valve (11) connects filler opening and the restriction (5) of relief valve (4) respectively, the oil outlet connected tank (2) of relief valve (4), another termination actuator (6) of restriction (5), the filler opening A of another termination selector valve (7) of secondary one-way valve (10), the oil outlet of auxiliary pump unit (8) meets the filler opening A of selector valve (7), the oil outlet O connected tank (2) of selector valve (7), the rear end that lower outside control mouth C connects the front end of restriction (5), upper outside control mouth B connects restriction (5), selector valve (7) is a gradual formula bi-bit bi-pass selector valve, comprise, bonnet (12), bottom flange (16), bonnet spring (13), spool (14), bottom flange spring (17), movable valve seat (18), filler opening A, oil outlet O, upper outside control mouth B, lower outside control mouth C, bonnet (12) is connected by bolt (15) with bottom flange (16), spool (14) has U-groove bevel (19), upper end blind hole (20) is had in spool (14) upper end, have lower end blind hole (21) in spool (14) lower end, lower end blind hole (21) has damping hole (22).
2. pressure differential control type stepless speed variator flow active control system according to claim 1, is characterized in that: the double action vane pump of main pump unit (9) and auxiliary pump unit (8) to be discharge capacity be 8ml/r.
3. pressure differential control type stepless speed variator flow active control system according to claim 1, is characterized in that: the range of regulation of relief valve (4) is 0 ~ 6MPa.
4. pressure differential control type stepless speed variator flow active control system according to claim 1, is characterized in that: to be an aperture be restriction (5)
metal aperture.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201310113576.4A CN103174816B (en) | 2013-04-03 | 2013-04-03 | A kind of pressure differential control type stepless speed variator flow active control system |
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| CN201310113576.4A CN103174816B (en) | 2013-04-03 | 2013-04-03 | A kind of pressure differential control type stepless speed variator flow active control system |
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| CN103174816A CN103174816A (en) | 2013-06-26 |
| CN103174816B true CN103174816B (en) | 2015-09-02 |
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| CN201310113576.4A Expired - Fee Related CN103174816B (en) | 2013-04-03 | 2013-04-03 | A kind of pressure differential control type stepless speed variator flow active control system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107605826A (en) * | 2017-10-16 | 2018-01-19 | 杭州诺祥科技有限公司 | Spool valve core type balanced valve treadmill driving control system |
| CN108626391A (en) * | 2018-05-14 | 2018-10-09 | 湘潭大学 | Automatic transmission flow active control system based on double pump source variable control technology |
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| CN101852283A (en) * | 2010-05-24 | 2010-10-06 | 镇江中浦冷辗科技有限公司 | Hydraulic stepless speed regulating device |
| CN102359621A (en) * | 2011-08-23 | 2012-02-22 | 湖南江麓容大车辆传动股份有限公司 | Electronic hydraulic control valve of transmission and stepless transmission comprising same |
| CN202543938U (en) * | 2012-04-16 | 2012-11-21 | 中南大学 | Hydraulic mechanism for eccentricity-adjustable hydraulic vibratory pile driver-extractor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10318152B4 (en) * | 2003-04-17 | 2018-07-05 | Volkswagen Ag | Oil supply device for the hydraulic circuit of a vehicle transmission or method for controlling the oil supply device |
| NL1038450C2 (en) * | 2010-12-15 | 2012-06-18 | Bosch Gmbh Robert | Hydraulic control system in a continuously variable transmission. |
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Patent Citations (3)
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| CN101852283A (en) * | 2010-05-24 | 2010-10-06 | 镇江中浦冷辗科技有限公司 | Hydraulic stepless speed regulating device |
| CN102359621A (en) * | 2011-08-23 | 2012-02-22 | 湖南江麓容大车辆传动股份有限公司 | Electronic hydraulic control valve of transmission and stepless transmission comprising same |
| CN202543938U (en) * | 2012-04-16 | 2012-11-21 | 中南大学 | Hydraulic mechanism for eccentricity-adjustable hydraulic vibratory pile driver-extractor |
Non-Patent Citations (1)
| Title |
|---|
| 无级变速器电液控制系统开发及关键技术研究;高帅;《中国博士学位论文全文数据库 工程科技Ⅱ辑》;20130315;C035-5的第55页-57页，附图3.1 * |
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