CN105134475A - Balance-adjustable bilateral drive axial plunger motor - Google Patents

Balance-adjustable bilateral drive axial plunger motor Download PDF

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Publication number
CN105134475A
CN105134475A CN201510470845.1A CN201510470845A CN105134475A CN 105134475 A CN105134475 A CN 105134475A CN 201510470845 A CN201510470845 A CN 201510470845A CN 105134475 A CN105134475 A CN 105134475A
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oil
row
balance
dual
adjustable
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CN201510470845.1A
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CN105134475B (en
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邓海顺
黄然
王传礼
何涛
黄坤
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Anhui University of Science and Technology
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Anhui University of Science and Technology
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Abstract

The invention discloses a balance-adjustable bilateral drive axial plunger motor which comprises a cylinder, an oil distribution disc, shells, a transmission shaft and a pressure intensity micro-adjustment device. Multiple rows of plunger holes evenly distributed around concentric circles are formed in the cylinder. The oil distribution disc is provided with multiple rows of oil suction ports and oil drainage ports. The oil drainage ports in each row of the oil distribution disc are communicated with an oil outlet through the corresponding shell. The oil suction ports in each row of the oil distribution disc are communicated with an oil inlet through the corresponding shell. The oil suction ports in the outer row or the oil outlets of the oil distribution disc are communicated with oil outlets of the pressure intensity micro-adjustment device. The stability of the bilateral drive axial plunger motor under high pressure and large loads can be well guaranteed, the design difficulty of the bilateral drive axial plunger motor can be greatly reduced, the service life of the bilateral drive axial plunger motor is prolonged, and the bilateral drive axial plunger motor is simple, feasible and good in application prospect and popularization value.

Description

A kind of dual-sided drive shafts of balance-adjustable is to piston motor
Technical field
The present invention relates to axial piston motor technical field, be specifically related to a kind of dual-sided drive shafts of balance-adjustable to piston motor.
Background technique
Axial piston motor is one of important hydraulic actuator in Hydraulic Power Transmission System, is widely used in the occasions such as engineering machinery, coal mine machinery, farm machinery, Aero-Space.
In view of axial existing axial piston motor working principle and structural feature, operationally, driving force is only present in its cylinder body side to existing axial piston motor all the time, causes its cylinder body by force unbalance, all there is larger offset loading force in oil distribution casing, transmission shaft, eccentric wear phenomenon is serious.Driving moment is only present in the side of cylinder body simultaneously, has larger impact to the robust motion of transmission shaft.Start and low cruise time not easily stablize, normal adjoint to creep, stop phenomenon, adverse influence is caused to the service behaviour of equipment and life-span, seriously constrains the using scope of axial piston motor.As can be seen here: existing axial piston motor exists the problems such as the comparatively large and low-speed stability of axial hydraulic force unbalance, transient torque pulsating quantity is poor all the time.
Along with the development of hydraulic transmission technology, especially the raising of pressure and the requirement of the increase of flow to axial piston motor performance also grow with each passing day, and dual-sided drive shafts produces under the guidance of this demand to piston motor.Dual-sided drive shafts due to its distinctive many swash plates ramp structure, all can produce the driving moment of equidirectional to piston motor in cylinder body both sides, thus drives the dynamic load of transmission shaft band to rotate.Because dual-sided drive shafts is as stressed in cylinder body, oil distribution casing, swash plate, the equal bilateral of transmission shaft to the key components and parts of piston motor, the problem of axial hydraulic force unbalance can be alleviated to a certain extent, improve the mechanical characteristic of key components and parts, improve the working stability of axial piston motor under low speed heavy load.But when bilateral hydraulic coupling is equal, because dual-sided drive shafts must be greater than interior row's arm of force to outer row's arm of force of piston motor, cause bilateral driving moment to vary in size.Simultaneously because the active area of the hydraulic coupling of interior row is also arranged little comparatively outward, also there is difference to a certain degree in the size of actual force, also further causes the difference of inside and outside row's driving moment size.As by changing dual-sided drive shafts to the physical dimension of the inside and outside row of piston motor, realize the complete equilibrium of key components and parts, then make design process complicated, difficulty strengthens.
Technical barrier is there is for above-mentioned, be necessary to propose a kind of new structural measure, change the size that its bilateral drives hydraulic coupling, completely equal to the complete equilibrium of piston motor key components and parts or both sides driving moment of dual-sided drive shafts is realized with this, thus reduction design difficulty, improve the performance of dual-sided drive shafts to piston motor further.This is also that the present invention puts forth effort problem to be solved.
Summary of the invention
For the deficiencies in the prior art, the invention provides a kind of dual-sided drive shafts of balance-adjustable to piston motor, can control in real time or adopt the control strategy matched with operating mode, improve dual-sided drive shafts further to the working stability under piston motor low speed heavy load.
Technological scheme
Technical problem to be solved by this invention can be come to be realize by the following technical programs:
A kind of dual-sided drive shafts of balance-adjustable is to piston motor, comprise cylinder body, oil distribution casing, housing and transmission shaft and pressure vernier device, be provided with in described cylinder body and arrange the plunger hole all distributed around concentric circumferences more, described oil distribution casing is provided with many row's inlet ports and oil drain out, the often row oil drain out of oil distribution casing is all communicated with and is linked into an oil outlet by described housing, the often row inlet port of oil distribution casing is communicated to a filler opening, outer row's inlet port of oil distribution casing or oil outlet are communicated to the oil outlet of pressure vernier device, pressure fine setting can be carried out to outer row's inlet port of oil distribution casing or oil drain out, make axial piston motor bilateral driving moment completely equal.
Described pressure vernier device rear end is connected with Returnning spring, and the Returnning spring the other end is connected with regulating handle.
Described described pressure vernier device is the spool of Proportional valve.
Inside and outside the ratio of described Proportional valve spool two ends face area and motor, organ timbering plug intraluminal fluid pressure application surface amasss proportional.
Inside and outside the ratio of described Proportional valve spool two ends face area and motor, organ timbering plug intraluminal fluid pressure application surface sum acting force arm is long-pending proportional.
Compared with prior art, beneficial effect of the present invention is:
The present invention adopts a kind of two filler openings to be equipped with pressure regulator, under making the hydraulic coupling of inside and outside row be in designated ratio value, can match with inside and outside row's acting force arm and active area; Adopt the inside and outside independent control mode of oil drain out simultaneously, connect other valve group and carry out independent pilot pressure ratio, can control in real time or adopt the control strategy matched with operating mode, improve dual-sided drive shafts further to the working stability under piston motor low speed heavy load; Hydraulic coupling is driven to control to the bilateral of filler opening, realize the stressed complete equilibrium of key components and parts or bilateral driving moment equal, compare existing axial piston motor and common bilateral driving axial piston motor, there is following advantage: one is adopt spool to control inside and outside row's pressure proportional, coordinate fine setting spring, really can realize the completely equal or stressed complete equilibrium of bilateral driving moment, thus farthest reduce output torque pulsation, improve the stability under low speed heavy load operating mode.Two is that the inside and outside difference of arranging the pressure of filler opening of employing adjustment realizes stress balance or driving moment is equal, being different from common bilateral driving axial piston motor adopts external and internal compositions size difference to realize stress balance or driving moment is equal, significantly reduces the design difficulty of pump key components and parts.Three is reserved external control hydraulic port, conveniently can detect outer row pressure power on the one hand, can match on the other hand with other valve group, utilizes feedback control to improve the effect of bilateral driving further.
Accompanying drawing explanation
Fig. 1 is the structural representation of dual-sided drive shafts to piston motor of the balance-adjustable of the present invention when having a double plunger;
Fig. 2 is the regulation and control schematic diagram of dual-sided drive shafts to piston motor of balance-adjustable when having double plunger;
Fig. 3 is a kind of condition regulation schematic diagram of dual-sided drive shafts to piston motor of the balance-adjustable with three organ timbering plugs;
Fig. 4 be the balance-adjustable with three organ timbering plugs dual-sided drive shafts to piston motor another in condition regulation schematic diagram.
Embodiment
For making the object of the embodiment of the present invention, technological scheme and advantage clearly, below in conjunction with the embodiment of the present invention, the technological scheme in the embodiment of the present invention is clearly and completely described, obviously, described embodiment is the present invention's part embodiment, instead of whole embodiments.Based on the embodiment in the present invention, those of ordinary skill in the art, not making the every other embodiment obtained under creative work prerequisite, belong to the scope of protection of the invention.
In Fig. 1,1. bolt one; 2. front case; 3. front shroud; 4. dust ring; 5. key; 6. transmission shaft; 7. bolt two; 8. bearing one; 9. external connection screw mouth and stifled; 10. axle sleeve; 11. proportional valve spools; 12. Returnning springs; 13. regulating handles; 14. left shells; 15. oil distribution casings; 16. right shell bodies; 17. springs; 18. plungers; 19. cylinder bodies; 20. bearings two; 21. swash plates; 22. piston shoes; 23. intermediate support assemblies; 24. back shrouds; 25. bolts three; 26. bolts four; P1 is filler opening; P2 is oil outlet;
In Fig. 2,1. proportional valve spool; 2. Returnning spring; 3. regulating handle; 4. transmission shaft; 5. oil distribution casing; 6. cylinder body; 7. outer organ timbering plug; 8. Inner organ timbering plug; 9. outside, arrange piston shoes; 10. row's piston shoes in; 11. swash plates; S1 is that interior organ timbering fills in hydraulic fluid port; S2 is that outer organ timbering fills in hydraulic fluid port.
In Fig. 3,1. proportional valve spool; 2. Returnning spring; 3. regulating handle; 4. transmission shaft; 5. oil distribution casing; 6. cylinder body; 7. outer organ timbering plug; 8. Inner organ timbering plug; 9. organ timbering plug in; 10. swash plate; S1 is that interior organ timbering fills in hydraulic fluid port; S2 is that middle organ timbering fills in hydraulic fluid port; S3 is that outer organ timbering fills in hydraulic fluid port;
In Fig. 4,1. proportional valve spool; 2. Returnning spring; 3. regulating handle; 4. transmission shaft; 5. oil distribution casing; 6. cylinder body; 7. outer organ timbering plug; 8. Inner organ timbering plug; 9. organ timbering plug in; 10. swash plate; S1 is that interior organ timbering fills in hydraulic fluid port; S2 is that middle organ timbering fills in hydraulic fluid port; S3 is that outer organ timbering fills in hydraulic fluid port.
Embodiment 1 is referring to Fig. 1, and to have double plunger actuation, the dual-sided drive shafts of balance-adjustable mainly comprises to piston motor: proportional valve spool 11, Returnning spring 12, regulating handle 13, external connection screw mouth and stifled 9, common double side axial piston motor.After high-voltage oil liquid is by oil inlet P 1, a point two-way carries out feed flow to plunger cavity: a part of high-voltage oil liquid is through A hydraulic fluid port and oil distribution casing 15, and directly internally row's plunger cavity carries out feed flow, produces driving force and driving moment, drives it to rotate in the side of cylinder body 19; Another part high-voltage oil liquid after the step-down of proportional valve spool 11, then carries out feed flow through B hydraulic fluid port and oil distribution casing 15 external row plunger cavity, produces and interior row's equidirectional driving force and driving moment, drives in another survey of cylinder body to cylinder body 19.
Referring to Fig. 1 and Fig. 2, the dual-sided drive shafts of visible balance-adjustable arrange in piston motor and the driving arm of force of outer row unequal, if inside and outside row's driving force is equal, then the driving moment of inside and outside row is inevitable unequal, if inside and outside row's plunger diameter number is equal, outer row's plunger diameter is greater than interior organ timbering plug, then driving force is also that outer row is larger.For realizing dual-sided drive shafts to piston motor better stationarity under low speed heavy load, the driving hydraulic coupling of inside and outside row can be made unequal, interior row pressure power is greater than outer row pressure power and proportional.It is as follows that it realizes principle: high-voltage oil liquid enters A mouth and B mouth respectively through P1 mouth, and the pressure of A mouth and B mouth acts on proportional valve spool 11 two ends respectively, when proportional valve spool 11 is in state of equilibrium, must have p aa f1+ F t=p ba f2equation of equilibrium, wherein p afor the pressure of A mouth, A f1for p aactive area on proportional valve spool 11, p bfor the pressure of B mouth, A f2for p bactive area on proportional valve spool 11, F tfor finely tuning the active force of spring.When A mouth pressure increases, ratio hair style 11 is moved to the left, and A mouth and B mouth passage increase, and pressure drop reduces, and B mouth pressure increases, and again reaches balance, namely meets p aa f1+ F t=p ba f2.Because fine setting spring force is much smaller than hydraulic coupling, therefore this equation of equilibrium also can be expressed as: p a: p b=A f2: A f1, namely A mouth and B mouth proportional all the time.
With reference to figure 1 and Fig. 2, A is set f1: A f2=A 1l 1: A 2l 2, wherein A 1for interior row drives hydraulic coupling p aactive area, l 1for the acting force arm of its correspondence, A 2for row drives hydraulic coupling p bactive area, l 2for the acting force arm of its correspondence, now p must be had 1a 1l 1=p 2a 2l 2, namely the driving moment of inside and outside row is completely equal, and the stationarity of motor under low speed heavy load operating mode can be made better.
With reference to figure 1 and Fig. 2, also can A be set f1: A f2=A 1: A 2, then p is had 1a 1=p 2a 2, namely the active force of inside and outside row is completely equal, cylinder body 19 be in quick condition, the dual-sided drive shafts of balance-adjustable can be made better to piston motor key components and parts mechanical property.
Referring to Fig. 1 and Fig. 2, by regulating handle 13, change the decrement of Returnning spring 12, the mechanical property of cylinder body or the balance of driving moment can be improved further.By the external pressure gauge of external connection screw mouth 9, regulating handle 13 control B mouth pressure together can be coordinated.External connection screw mouth 9 is connected with other valve group with oil inlet P 1, can the force value of accurately control A mouth and B mouth further, also can realize real-time control simultaneously.
Embodiment 2 referring to Fig. 3,4 for the dual-sided drive shafts with the balance-adjustable of three organ timbering plugs is to two kinds of piston motor different regulation and control schematic diagram.
Referring to Fig. 3, the fluid centering row plunger cavity S2 feed flow at hydraulic fluid port A place, the fluid at hydraulic fluid port B place internally arranges plunger cavity S1 and outer row's plunger cavity S3 feed flow.Middle row's plunger cavity actual size is all larger than interior row's plunger cavity size, outer row's plunger cavity size, and after pressure controlling, in can ensureing, the moment sum at the moment at organ timbering plug place and interior row, outer organ timbering plug place keeps balancing, and makes cylinder body completely floating.When plunger cavity pressure surge, when making cylinder body 6 moment unbalance, regulated by regulating handle 3 pairs of Returnning springs 2, cylinder body 6 is restored balance state.
The fluid at Fig. 4, hydraulic fluid port A place externally arranges plunger cavity S3 feed flow, and the fluid at hydraulic fluid port B place internally arranges plunger cavity S1 and middle row's plunger cavity S2 feed flow.Outer organ timbering plug cavity pressure acting force arm is maximum, and interior row, middle organ timbering plug cavity pressure acting force arm are less, after pressure controlling, can ensure the moment at outer organ timbering plug place and interior row, the moment sum at middle organ timbering plug place keeps balancing, make cylinder body completely floating.When plunger cavity pressure surge, when making cylinder body 6 moment unbalance, regulated by regulating handle 3 pairs of Returnning springs 2, cylinder body 6 is restored balance state.
The dual-sided drive shafts of balance-adjustable of the present invention is control its filler opening place pressure to piston motor, and this control mode can control its oil outlet place pressure equally, makes cylinder body suffered back of the body oil pressure equalising torque, thus makes cylinder body complete equilibrium.Meanwhile, this pressure controlling mode is also applicable to arrange axial piston pump more, makes its cylinder body completely floating.
It should be noted that, in this article, such as term " comprises ", " comprising " or its any other variant are intended to contain comprising of nonexcludability, thus make to comprise the process of a series of key element, method, article or equipment and not only comprise those key elements, but also comprise other key elements clearly do not listed, or also comprise by the intrinsic key element of this process, method, article or equipment.When not more restrictions, the key element limited by statement " comprising ... ", and be not precluded within process, method, article or the equipment comprising described key element and also there is other identical element.
Above embodiment only in order to technological scheme of the present invention to be described, is not intended to limit; Although with reference to previous embodiment to invention has been detailed description, those of ordinary skill in the art is to be understood that: it still can be modified to the technological scheme described in foregoing embodiments, or carries out equivalent replacement to wherein portion of techniques feature; And these amendments or replacement, do not make the essence of appropriate technical solution depart from the spirit and scope of various embodiments of the present invention technological scheme.

Claims (5)

1. the dual-sided drive shafts of a balance-adjustable is to piston motor, comprise cylinder body, oil distribution casing, housing and transmission shaft and pressure vernier device, it is characterized in that: be provided with in described cylinder body and arrange the plunger hole all distributed around concentric circumferences more, described oil distribution casing is provided with many row's inlet ports and oil drain out, the often row oil drain out of oil distribution casing is all communicated with and is linked into an oil outlet by described housing, the often row inlet port of oil distribution casing is communicated to a filler opening, outer row's inlet port of oil distribution casing or oil outlet is communicated to the oil outlet of pressure vernier device.
2. the dual-sided drive shafts of balance-adjustable according to claim 1 is to piston motor, it is characterized in that, described pressure vernier device rear end is connected with Returnning spring, and the Returnning spring the other end is connected with regulating handle.
3. the dual-sided drive shafts of balance-adjustable according to claim 1 and 2 is to piston motor, it is characterized in that, described pressure vernier device is the spool of Proportional valve.
4. the dual-sided drive shafts of balance-adjustable according to claim 3 is to piston motor, it is characterized in that: inside and outside the ratio of described Proportional valve spool two ends face area and motor, organ timbering plug intraluminal fluid pressure application surface amasss proportional.
5. the dual-sided drive shafts of balance-adjustable according to claim 3 is to piston motor, it is characterized in that: inside and outside the ratio of described Proportional valve spool two ends face area and motor, organ timbering plug intraluminal fluid pressure application surface sum acting force arm is long-pending proportional.
CN201510470845.1A 2015-08-04 2015-08-04 A kind of dual-sided drive shafts of balance-adjustable are to piston motor Active CN105134475B (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106593972A (en) * 2016-11-25 2017-04-26 江正庆 Numerical control hydraulic flexible system

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0389644A4 (en) * 1988-10-03 1992-05-20 Hitachi Construction Machinery Co., Ltd. Variable capacitance, oblique spindle type hydraulique machine
CN2184797Y (en) * 1993-12-02 1994-12-07 韩旭升 Piston pump of electric oi filler
CN2706641Y (en) * 2004-05-20 2005-06-29 王雪敏 Manual gas proportion valve
CN202531374U (en) * 2012-04-26 2012-11-14 安徽理工大学 Balance-type high-flow axial plunger pump
CN103557153A (en) * 2013-11-20 2014-02-05 沈阳工业大学 Electric-hydraulic proportional displacement regulating mechanism of axial plunger hydraulic pump
CN104358657A (en) * 2014-11-03 2015-02-18 安徽理工大学 Two-side driving balance type low-speed large-torque axial plunger motor
CN204827788U (en) * 2015-08-04 2015-12-02 安徽理工大学 But two side drive axial piston motor of balancing

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0389644A4 (en) * 1988-10-03 1992-05-20 Hitachi Construction Machinery Co., Ltd. Variable capacitance, oblique spindle type hydraulique machine
CN2184797Y (en) * 1993-12-02 1994-12-07 韩旭升 Piston pump of electric oi filler
CN2706641Y (en) * 2004-05-20 2005-06-29 王雪敏 Manual gas proportion valve
CN202531374U (en) * 2012-04-26 2012-11-14 安徽理工大学 Balance-type high-flow axial plunger pump
CN103557153A (en) * 2013-11-20 2014-02-05 沈阳工业大学 Electric-hydraulic proportional displacement regulating mechanism of axial plunger hydraulic pump
CN104358657A (en) * 2014-11-03 2015-02-18 安徽理工大学 Two-side driving balance type low-speed large-torque axial plunger motor
CN204827788U (en) * 2015-08-04 2015-12-02 安徽理工大学 But two side drive axial piston motor of balancing

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106593972A (en) * 2016-11-25 2017-04-26 江正庆 Numerical control hydraulic flexible system

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