CN105756850A - Intermediate-speed large-torque radial plunger hydraulic motor - Google Patents

Intermediate-speed large-torque radial plunger hydraulic motor Download PDF

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Publication number
CN105756850A
CN105756850A CN201610242447.9A CN201610242447A CN105756850A CN 105756850 A CN105756850 A CN 105756850A CN 201610242447 A CN201610242447 A CN 201610242447A CN 105756850 A CN105756850 A CN 105756850A
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China
Prior art keywords
oil
ring
retaining ring
housing
type motor
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Application number
CN201610242447.9A
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Chinese (zh)
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CN105756850B (en
Inventor
叶春浓
蒋志坚
葛正菊
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INTRA-ITALIA HYDRAULICS (FOSHAN SHUNDE) Co Ltd
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INTRA-ITALIA HYDRAULICS (FOSHAN SHUNDE) Co Ltd
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Priority to CN201610242447.9A priority Critical patent/CN105756850B/en
Publication of CN105756850A publication Critical patent/CN105756850A/en
Priority to PCT/CN2017/080515 priority patent/WO2017181907A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/22—Reciprocating-piston liquid engines with movable cylinders or cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/22—Reciprocating-piston liquid engines with movable cylinders or cylinder
    • F03C1/223—Reciprocating-piston liquid engines with movable cylinders or cylinder having cylinders in star or fan arrangement, the connection of the pistons with an actuated element being at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0406—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0415—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0444—Particularities relating to the distribution members to plate-like distribution members

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Support Of The Bearing (AREA)

Abstract

The invention relates to an intermediate-speed large-torque radial plunger hydraulic motor which comprises a casing (1), a crankshaft (2), a roller (3), a bearing bush (4), a cylinder head (5), a telescopic sleeve (6), a retainer ring (7), a hanger rod (8) and a drive shaft (10).The telescopic sleeve (6) is arranged along the radial direction of the bearing bush (4), and the upper end and the lower end of the telescopic sleeve (6) are respectively abutted against an external spherical surface (501) of the cylinder head (5) and an external spherical surface (402) of the bearing bush (4).The lower end of the telescopic sleeve (6) is closely attached to the external spherical surface (402) of the bearing bush (4) by the retainer ring (7).The upper end of the telescopic sleeve (6) is closely attached to the external spherical surface (501) of the cylinder head (5) by the hanger rod (8).Two ends of the drive shaft (10) are respectively connected with the crankshaft (2) and an oil distributing mechanism (9).The roller (3) is inserted in an inner bore (401) of the bearing bush; and the crankshaft (2) comprises an eccentric section (201).Compared with the prior art, the radial plunger hydraulic motor has the advantages of highly increased revolution speed and compact structure.

Description

A kind of middling speed high pulling torque radial plunger type motor
Technical field
The present invention relates to technical field of hydraulic elements, specifically a kind of middling speed high pulling torque radial plunger type motor.
Background technology
Radial plunger type motor typical construction is plunger is radial distribution along driving axle, and plunger motion plane is vertical with driving axle, and it has the remarkable advantages that discharge capacity is big, and moment of torsion is big, directly band dynamic load can start, be particularly suitable for the application scenario of low-speed big.
But, actually used on market today showing, common radial plunger type motor uses rotating speed lower than 300r/min.By hydraulic motor industry with 500r/min for boundary, will be above 500r/min and be classified as high-speed motor, the viewpoint sanctified by usage of zero motor it is classified as lower than 500r/min, the radial plunger type motor major part sold on market today should be classified as low-speed big radial plunger type motor, high-speed motor higher than 500r/min is the axial plunger type motor that moment of torsion is less than normal mostly, it is generally required to could band dynamic load be started by deceleration link.Along with the progress of science and technology, market occurs in that turn up 300～1000r/min, corresponding discharge capacity 4000～200mL/r, the thriving demand of the energy directly middling speed high-torque hydraulic motor that bringing onto load starts.
From above-mentioned to hydraulic motor simple analysis, what can meet the direct bringing onto load startup of middling speed high pulling torque can only be radial plunger structure, and all kinds of low-speed big radial plunger type motors are along with the raising using rotating speed now, there is various problem in capital, instructions for use can not be met, even if there being the hydraulic motor that can deserve to be called individually middling speed high pulling torque to there is also various defect.
Fig. 1 and Fig. 2 is the structural representation of a kind of crankshaft connecting low-speed big radial plunger type motor of prior art, and its structural representation can be indicated in the catalog of relevant manufacturers.Including housing 1, protecgulum 2, bent axle 3, roller 4, bearing block 5, connecting rod 6, retaining ring 7, piston 8, cylinder cap 9, oil distribution mechanism 10.Bent axle 3, roller 4, bearing block 5 constitutes a roller bearing structure, and connecting rod 6 is rigidly connected on bearing block 5 external cylindrical surface 501 by each retaining ring 7 in both sides, the bulb 602 of connecting rod 6 is arranged in the ball-and-socket 801 of piston 8, and piston 8 is arranged in the Cylinder inner bore 901 of cylinder cap 9.During work, hydraulic oil (not noting in figure) is assigned to each cavity volume surrounded by piston 8 and cylinder cap 9 inner chamber 902 by oil distribution mechanism successively, hydraulic oil promotes piston 8 slide downward in the Cylinder inner bore 901 of cylinder cap 9, the piston 8 of slide downward promotes connecting rod 6 to move downward, connecting rod 6 move downward while around its bulb 602 the centre of sphere along be perpendicular to bent axle 3 axis x direction swing and promote bent axle 3 to rotate through bearing block 5, roller 4.Crankshaft connecting low-speed big radial plunger type motor low price, it is applied widely in speed operation field, it is one of yield is maximum in the world low speed high torque hydraulic motor, but along with the raising of rotating speed, the hydraulic motor of this version exists following shortcoming:
1, the outer surface 501 of bearing block 5 is a face of cylinder, and the inner concave 603 of the connecting rod 6 coordinated with bearing block 5 face of cylinder 501 is still the face of cylinder, and between the face of cylinder, laminating can not retrain along cylinder axis direction, i.e. the degree of freedom in axle y direction.Therefore, along with the raising of working speed, the stationkeeping ability of connecting rod 6 is poor, poor stability.
2, connecting rod 6 and retaining ring 7 are entirely being rigidly connected of mechanical component, there is gap between groove 601 and the retaining ring endoporus 701 of connecting rod 6, and along with the raising of rotating speed, centrifugal force increases, and there is mechanical impact between connecting rod 6 and retaining ring 7, produces noise.
3, as shown in Figure 2, along with connecting rod 6 swings along the axis x direction being perpendicular to bent axle 3 around the centre of sphere of its bulb 602, there is the angle of cut θ of mechanical periodicity in the axis m of the connecting rod 6 and axis n of piston 8, there is periodic side force in piston 8, this side force makes the Cylinder inner bore 901 of cylinder cap 9 produce irregular abrasion, after abrasion, circle becomes oval, as it is shown on figure 3, rotating speed is more high, the more high oval abrasion of pressure is more serious.
4, from the characteristics of motion of above-mentioned connecting rod 6, the motive force of bent axle 3 is had the fluctuation by the change of cosine rule by connecting rod 6, and namely motive force is equal to Fcos θ, and wherein F little is together decided on by piston 8 diameter and hydraulic oil pressure are powerful, it follows that bent axle 3 exports moment of torsion there is fluctuation.
5, except the defect in said structure principle, the motor of this version there is also technologic deficiency.Arranging two on bent axle 3 for retraining the roller 4 step 301 along axle y direction degree of freedom, distance dimensional tolerance and surface smoothness between 302, two steps 301 and 302 all have higher requirement, inconvenience is brought to processing, in like manner, the step 502,503 of bearing block 5 also brings inconvenience to processing.
Fig. 4 is the invention of Calzoni company of Italy, Shuande, Foshan favorite hydraulic pressure company limited obtains the structural representation of a kind of slip expansion pendulum cylinder-type low-speed big radial plunger type motor of the prior art of its production permit, including housing 1, protecgulum 2, bent axle 3, oil cylinder 4, piston 5, spring 6, cylinder cap 7, spring cup 8, spring base 9, oil distribution mechanism 10.Bent axle 3, cylinder cap 7 is respectively equipped with spherical outside surface 301, and 701, oil cylinder 4, piston 5 is respectively equipped with Internal Spherical Surface 401,501.Spring 6 is by spring base 9, and the spherical outside surface 701 of the Internal Spherical Surface 401 of oil cylinder 4 with the spherical outside surface 301 of bent axle 3 and the Internal Spherical Surface 501 of piston 5 and cylinder cap 7 is adjacent to by spring cup 8 respectively.Oil cylinder 4 and piston 5 coaxial cooperation, cooperation axis is y, constitute one be only capable of along axis y do telescopic slide and with axis x vertical plane in around the centre of sphere O of cylinder cap 7 sphere 7011The telescopic oscillating tube-in-tube structure swung.Cylinder cap 7, piston 5, oil cylinder 4, bent axle 3 constitutes a sealed volume, and during work, oil distribution mechanism 10 hydraulic oil being assigned to successively enters this sealed volume, and the hydraulic pressure oil column that cavity volume surrounds pushes directly on bent axle 3 and rotates.Bent axle 3 rotates a circle, and stretches once between oil cylinder 4 and piston 5, and spring 6 is also followed and stretched once.Compared with above-mentioned crankshaft connecting low-speed big radial plunger type motor, slip expansion pendulum cylinder-type low-speed big radial plunger type motor has obvious advantage:
1, between oil cylinder 4 and piston 5 only along the flexible of axis y and with axis x vertical plane in around the centre of sphere O of cylinder cap 7 sphere 7011The telescopic oscillating motion swung, oil cylinder 4 remains coaxial with piston 5, is absent from side force between the two, it means that be absent from oval abrasion.
2, hydraulic oil pushes directly on bent axle 3 and rotates, and thrust size is together decided on by piston 5 diameter and hydraulic oil pressure, is absent from the fluctuation of power that crankshaft connecting low-speed big radial plunger type motor causes because of the inherent character of organisation conversion principle and moment of torsion.
But along with the raising of rotating speed, the slip expansion pendulum cylinder-type low-speed big radial plunger type motor of prior art shown in Fig. 4 still suffers from following shortcoming:
1, as the above analysis, bent axle 3 rotates a circle, spring 6 is flexible, and once rotating speed is more high, and spring 6 stretching frequency is more high, more easy fatigue fracture, therefore, and one of 6 one-tenth of spring bottleneck improving motor rotary speed.
2, stretching along with spring 6, between oil cylinder 4 and bent axle 3, the contact stress generating period change between piston 5 and cylinder cap 7, by contact mechanics knowledge it can be seen that alternation contact stress is easier to make contact surface produce fatigue rupture than Static Contact stress.
3, forming a sliding friction pair between oil cylinder Internal Spherical Surface 401 and bent axle spherical outside surface 301, by tribology principle it can be seen that the material wear-resistant limit is by the restriction of PV value between friction pair, wherein P is the normal pressure between friction pair, and V is the relative sliding velocity between friction pair.Along with the raising of rotating speed, V increases therewith, abrasion aggravation, and therefore friction pair abrasion is to improve the bottleneck that this version motor rotary speed is the most serious.
For the shortcoming of above-mentioned slip expansion pendulum cylinder-type low-speed big radial plunger type motor, relevant manufacturers has carried out various improvement:
The application publication number that on February 4th, 2015 announces is that CN104329217A discloses a kind of flexible tilt cylinder type hydraulic motor and eccentric shaft sphere processing method thereof, process means is passed through in this invention, bent axle sphere processes tiny liquid storage hole to improve its self-lubricating property, though friction can be reduced to a certain extent, improve rotating speed, but the physics fact of sliding friction between oil cylinder and bent axle sphere does not change, still by the restriction of friction pair PV value.
The application publication number that on April 3rd, 2013 announces is that CN103014587A discloses a kind of method spraying molybdenum coating at Crankshaft fever sensation of the face, this invention by spraying layer of metal coating on bent axle sphere, to increase its self lubricity and wearability, the method obtains good effect on huge discharge (3600ml/r and more than) hydraulic motor, but it is the same with the inventive method that above-mentioned CN104329217A announces, the physics fact of sliding friction between oil cylinder and bent axle sphere does not change, still by the restriction of friction pair PV value, middling speed operating mode still cannot be competent at.
American documentation literature US5967018 discloses a solution, such as Fig. 5.Arranging a set of radial expansion sleeve 3 between cylinder cap 1 and bent axle 2, extension sleeve 3 respectively arranges an Internal Spherical Surface, cylinder cap 1 and bent axle 2 containing oil cylinder 4. and piston 5, oil cylinder 4 and piston 5 and respectively arranges a spherical outside surface；Oil cylinder 4 is applied elastic force by spring 6, makes oil cylinder 4 Internal Spherical Surface and bent axle 2 spherical outside surface be adjacent to；Piston 5 is applied elastic force by spring 7, makes piston 5 Internal Spherical Surface and cylinder cap 1 spherical outside surface be adjacent to；Spring 6 and spring 7 do not change decrement with the rotation of bent axle 2, therefore that the pretightning force of contact surface is constant, improve the force-bearing situation of contact surface correlated parts, it is to avoid fatigue fracture and aggravation sphere abrasion phenomenon occur along with the raising spring of rotating speed.But the program still suffers from following shortcoming:
1, spring 6 and spring 7 are arranged at the periphery of extension sleeve 3, add motor dimension, especially significantly increase the size of cylinder cap 1.
2 is the same with aforementioned schemes, and between oil cylinder 4 and bent axle 2 sphere, the physics fact of sliding friction does not change, and still by the restriction of friction pair PV value, still cannot be competent at middling speed operating mode.
American documentation literature US7267042B2 is disclosed another kind of solution after american documentation literature 5967018, such as Fig. 6.The spring that american documentation literature 5967018 is arranged at outside piston is moved to internal piston by the program, by components such as peg, peg rings, spring carried out pretension, decrease motor dimension, but during motor running, the friction pair that oil cylinder and bent axle contact surface form is still sliding friction pair, it is impossible to competent middling speed operating mode.
Fig. 7 is the structural representation of a kind of pendulum cylinder-type high pulling torque radial plunger type motor that Sai company of Italy produces, including bent axle 1, roller 2, bearing holder (housing, cover) 3, tilt cylinder 4, piston 5, retaining ring 6, butterfly spring 7, procapsid 8, back casing 9, oil distribution mechanism 10 etc..Tilt cylinder 4 is by two gudgeons 401,402 are supported in procapsid 8 and back casing 9 hole, during work, tilt cylinder 4 swings around gudgeon 401,402, and piston 5 only does relative stretching motion with tilt cylinder 4, thus eliminating the piston 5 lateral pressure to tilt cylinder 4, reduce friction, eliminate oval wear phenomenon, improve mechanical efficiency.Adopting the sliding friction that roller bearing structure becomes above-mentioned link-type and slip expansion pendulum cylinder-type motor between piston 5 and bent axle 1 is rolling friction, is substantially reduced frictional force and caloric value.Bearing holder (housing, cover) 3 two ends respectively arrange a butterfly spring 7, and retaining ring 6 is applied elastic force by butterfly spring 7, retaining ring 6 are buckled on the groove of piston 5, it is prevented that piston 5 and bearing holder (housing, cover) 3 depart from.Piston 5 and bearing holder (housing, cover) 3 are sphere-contact, improve centering and stability.This version motor obtains in middling speed field and applies effect preferably, but still there is following shortcoming:
1, tilt cylinder swings around the gudgeon being supported in forward and backward housing, oscillation center is in enclosure interior, and pendulum radius is little, analyzes at its monograph " low speed high torque hydraulic motor Design Theory and calculating " according to Chen Zhuoru professor, pendulum radius is more little, and motor torsional moment and speed ripple are more big.
2, gudgeon is cantilever beam structure, there is bending stress, and mechanical characteristic is bad.
3, for the contact stress of less tilt cylinder gudgeon, trunnion diameter is relatively big, and weight is big, adds tilt cylinder movement inertia, and rotating speed is more high, and its negative effect is more big.
4, internal piston arranges a damping hole, the thin-wall construction of piston non-fully hollow, and weight is big, its shortcoming such as disadvantages mentioned above 3.
5, arranging two cantilever trunnion on column type tilt cylinder, the axiality of two gudgeons, fineness, case hardness all have higher requirement, and therefore processing technology is bad.
6, the spring of elastic force is provided to be butterfly spring to retaining ring, though compacter than helical spring, but still have the space of improvement, can motor dimension is made more compact.
American documentation literature US8206130B2 discloses a kind of radial plunger type motor with high speed capability, its population structure is similar to the pendulum cylinder-type high pulling torque radial plunger type motor that above-mentioned Sai company produces with operation principle, gudgeon is offered some oil grooves, gudgeon is carried out forced feed lubrication, also having offered lubrication groove on oil distribution casing, described two measures improve friction lubricating characteristic simultaneously.But structure as shown in Figure 7 above, trunnion configuration inherent defect does not change, and oil distribution mechanism does not possess automatic compensation ability.
Summary of the invention
The technical problem to be solved in the present invention is in that: for the defect of prior art, it is provided that a kind of middling speed high pulling torque radial plunger type motor.
The technical scheme is that and be achieved in that: a kind of middling speed high pulling torque radial plunger type motor, including housing, the bent axle of external output speed and moment of torsion, it is coated at the roller of the eccentric shaft part of bent axle, it is placed in roller in the endoporus of bearing holder (housing, cover), the radially uniform cylinder cap being anchored on housing of star, along the extension sleeve that bearing block radial distribution and upper and lower side offset with the spherical outside surface of cylinder cap and the spherical outside surface of bearing holder (housing, cover) respectively, the lower end of extension sleeve is close to all the time the retaining ring of the spherical outside surface of bearing holder (housing, cover), the upper end of extension sleeve is close to all the time the peg of cylinder cap spherical outside surface, the power transmission shaft that two ends are connected with bent axle and oil distribution mechanism respectively.Described extension sleeve comprises oil cylinder and piston, described oil cylinder and described piston coaxial and coordinates, and axis z is all the time by the centre of sphere O of the spherical outside surface of cylinder cap1Centre of sphere O with the spherical outside surface of bearing holder (housing, cover)2, during work, oil cylinder and piston are along the centre of sphere O of z-axis stretching motion and the sphere around cylinder cap1Swing.Described bent axle, roller, bearing holder (housing, cover) constitute a rolling bearing structure.Also include retaining ring, retaining ring pressing plate, the elastic rubber ring that is arranged between retaining ring and retaining ring pressing plate, being close to retaining ring pressing plate and be fastened in the circlip in described bearing holder (housing, cover) groove, the spherical outside surface of the Internal Spherical Surface of oil cylinder Yu bearing holder (housing, cover) is adjacent to by described circlip；Also including pallet, self-locking nut, peg, peg ring, butterfly spring, spring base, circlip, piston Internal Spherical Surface and cylinder cap spherical outside surface are adjacent to by described pallet, self-locking nut, peg, peg ring, butterfly spring, spring base, circlip；Also include oil distribution mechanism, described oil distribution mechanism includes oil-distributing plate, oil distribution casing, floating ring, butterfly spring, bonnet, power transmission shaft traverse housing and the oil-distributing plate other end that one end is hinged with bent axle are hinged with oil distribution casing, during work, bent axle, power transmission shaft, oil distribution casing synchronizes to rotate forward or backwards around axle x, floating ring is directly pressed on oil distribution casing by one end and the bonnet butterfly spring that the other end and floating ring offset that offsets, and then indirectly oil distribution casing is pressed on oil-distributing plate, play initial sealing and wear-compensating effect, namely after abrasion occurring between floating ring and oil distribution casing or between oil distribution casing and oil-distributing plate, under the elastic force effect of butterfly spring, between floating ring and oil distribution casing, remain in that between oil distribution casing and oil-distributing plate and be adjacent to.Two ends, described bearing holder (housing, cover) left and right offset with the step surface of housing and gap, protecgulum left side respectively, and namely bearing holder (housing, cover) is retrained along the degree of freedom in axle y direction by described step surface and described left side, but bearing holder (housing, cover) can rotate freely around axle x again together with bent axle.
Further, the described oil cylinder external diameter near Internal Spherical Surface one end arranges a groove, and the diameter A of described groove is more smaller than oil cylinder internal diameter B.
Further, the ratio of the diameter A of described groove and oil cylinder internal diameter B approximates 0.8～0.85, and the ratio of the truncated-spherical size C of oil cylinder and the diameter A of groove is not less than 0.5.
Further, the ratio of the truncated-spherical size C of described oil cylinder and the diameter A of groove is 0.7～0.8.
Further, described piston is set to hollow and thin-walled column structure.
Further, the eccentric shaft part left end of described bent axle arranges one around the convex annular step of axle y.
Further, the eccentric shaft part of described bent axle arranges 2-4 road compensating groove.
Further, the endoporus of described bearing holder (housing, cover) is set to one without the unthreaded hole on boss rank.
Further, the endoporus of described bearing holder (housing, cover) arranges 2 road compensating grooves.
Further, arranging an elastic rubber ring and place the groove of elastic rubber ring between described retaining ring and retaining ring pressing plate, groove both may be disposed in retaining ring, it is possible to is arranged on retaining ring pressing plate.
Further, the elastic rubber ring material being arranged between retaining ring and retaining ring pressing plate is nitrile rubber, and elastic rubber ring cross section can be circular, square, star or other shape.
Further, described retaining ring arranges an endoporus, and retaining ring pressing plate arranges a boss, and the endoporus of retaining ring coordinates with the boss of retaining ring pressing plate, and coordinating axis is axle y.
Further, the periphery of described oil cylinder lower end, namely offset with the spheric seat periphery of one end arranges a groove, retaining ring is fastened on the groove that oil cylinder lower end is peripheral, by retaining ring, the elastic rubber ring that is arranged between retaining ring and retaining ring pressing plate, retaining ring pressing plate, is close to retaining ring pressing plate and the spherical outside surface of the Internal Spherical Surface of oil cylinder Yu bearing holder (housing, cover) is adjacent to by the circlip that is fastened in bearing holder (housing, cover) groove.
Further, described piston inner hole arranges a ring-shaped step, and by the pallet offseted with ring-shaped step, with the self-locking nut of the threaded engagement of peg, peg, piston Internal Spherical Surface and cylinder cap spherical outside surface are adjacent to by peg ring, butterfly spring, spring base, circlip.
Further, described peg and peg ring are respectively provided with a spherical outside surface and Internal Spherical Surface, and two spheres offset, and can do relative sliding.
Further, described peg arranges 2-4 oil through, size and the quantity basis motor displacement size in hole and determine.
Further, the centre of sphere O of the spherical outside surface of described cylinder cap1It is arranged on the outside of cylinder cap entity.
Further, the centre of sphere of the sphere of described cylinder cap, peg, peg ring, four parts of piston is concentric.
Further, described oil distribution casing and the described oil-distributing plate plane that offsets is provided with three concentric ring bands, it is outer ring seal band, medium ring band, inner ring seal band respectively, on described outer ring seal band outer in staggered be provided with two row's oilholes and, often row's oilhole quantity is 2 or more than 2, the external envelope radius of circle of described interior row's oilhole is bigger than the interior envelope radius of circle of described outer shroud oilhole, i.e. R1> R2。
Further, interlocking and be provided with two row's oilholes in outer on described medium ring band, often row's oilhole quantity is 2 or more than 2, and the external envelope radius of circle of described interior row's oilhole is bigger than the interior envelope radius of circle of described outer shroud oilhole, i.e. R3> R4。
Further, on described inner ring seal band, outer interior interlocking is provided with two row's oilholes, often row's oilhole quantity is 2 or more than 2, and the external envelope radius of circle of described interior row's oilhole is bigger than the interior envelope radius of circle of described outer shroud oilhole, i.e. R5 > R6.
The present invention compared with prior art, has the following advantages and beneficial effect:
1, the present invention adopts extension sleeve structure, the oil cylinder piston coaxial cooperation of composition extension sleeve, oil cylinder and its axis of piston of doing relative telescoping movement overlap all the time, eliminate the phenomenon of side force that link-type motor produces and oval abrasion because having an angle of cut along with the relative motion axis of piston Yu connecting rod.
2, the hydraulic pressure oil column surrounded by bearing block, oil cylinder, piston, cylinder cap pushes directly on bearing block and bent axle rotation, compared with the pendulum cylinder-type motor of the link-type of prior art and Sai company of Italy, improves mechanical efficiency and reliability.
3, oil cylinder, piston is thin-wall tubular structure, and compared with prior art, quality is lighter, and movement inertia is less, is therefore more suitable for high speed operating mode, and meanwhile, its processing technique is simpler.
4, between oil cylinder and bearing block, being sphere-contact between piston and cylinder cap, compared with coordinating with the face of cylinder of link rod structure, centering and stability are better, and compared with trunnion configuration, mechanical characteristic is better.
5, the sliding friction adopting the slip expansion pendulum cylinder-type motor of roller bearing structure change Calzoni company of Italy and the favorite company limited in Shuande, Foshan prior art between oil cylinder and bent axle is rolling friction, it is substantially reduced frictional force and caloric value, but it is different with the prior art of crankshaft connecting rod type with Sai company of Italy to be embodied as in details again.
6, adopting elastic rubber ring to replace butterfly spring that retaining ring is applied pretension, compared with prior art, decrease motor axial dimension, motor is more compact, and meanwhile, rubber ring has the damping action absorbing energy, can play the good effect absorbing vibration and noise.
7, the oscillation center of extension sleeve is arranged on the outside of cylinder cap entity, increases the pendulum radius of extension sleeve, compared with prior art, decrease motor rotary speed and torque ripple.
8, bent axle with bearing block in the axial direction without relative position constraint relation, the axially and radially degree of freedom of bent axle is retrained by being arranged at the housing two bearings with protecgulum, bearing block axial freedom is retrained by housing boss face and protecgulum left side, therefore the boss rank retraining roller and bearing block on crankshaft eccentric shaft part can be removed, one boss rank of crankshaft eccentric shaft part position temporarily and arrange when being only assembly and disassembly, functional effect is not played during work, dimensional accuracy and surface smoothness requirements are not high, and therefore Crankshaft Machining is convenient.
9, offering forced feed lubrication oilhole and counterbalance spring on oil distribution casing, greasy property is better, and reliability is higher.
Accompanying drawing explanation
Below in conjunction with accompanying drawing, the present invention is further described.
Fig. 1 is a kind of crankshaft connecting low-speed big radial plunger type motor structural representation of prior art.
Fig. 2 is the A-A sectional view of Fig. 1.
Fig. 3 is crankshaft connecting low-speed big radial plunger type motor ellipse abrasion schematic diagram.
Fig. 4 is a kind of slip expansion pendulum cylinder-type low-speed big radial plunger type motor structural representation of prior art.
Fig. 5 is a solution structural representation disclosed in american documentation literature US5967018.
Fig. 6 is a solution structural representation disclosed in american documentation literature US7267042B2.
Fig. 7 is the structural representation of a kind of pendulum cylinder-type high-torque hydraulic motor that Sai company of Italy produces.
Fig. 8 is the structural representation of a kind of middling speed high pulling torque radial plunger type motor of the present invention.
Fig. 9 is cylinder structure schematic diagram of the present invention.
Figure 10 is hook rail structure schematic diagram of the present invention.
Figure 11 is crankshaft structure schematic diagram of the present invention.
Figure 12 is the partial enlarged drawing I of Fig. 8.
Figure 13 is oil distribution casing structural representation of the present invention.
Figure 14 is the A-A sectional view of Figure 13.
Figure 15 is the partial enlarged drawing II of Figure 13.
Figure 16 is that oil distribution casing oilhole of the present invention arranges schematic diagram.
Wherein in figure:
1. housing 101. casing step face
2. eccentric shaft part 202. convex annular step 203. step end face 204. compensating groove of bent axle 201.
3. roller
4. bearing holder (housing, cover) 401. endoporus 402. bearing holder (housing, cover) spherical outside surface
5. cylinder cap 501. cylinder cap spherical outside surface
6. extension sleeve
7. retaining ring
8. peg 801. screw thread 802. spherical outside surface 803. oil through
9. oil distribution mechanism
10. power transmission shaft
11. oil cylinder 1101. oil cylinder Internal Spherical Surface 1102. groove
12. piston 1201. piston Internal Spherical Surface 1202. ring-shaped step
13. retaining ring pressing plate
14. elastic rubber ring
15. the circlip in bearing holder (housing, cover) groove
16. pallet
17. self-locking nut
18. peg ring 1801. Internal Spherical Surface
19. butterfly spring
20. spring base
21 circlips
22. oil-distributing plate
23. oil distribution casing 2301. outer ring seal band 2302. medium ring band 2303. inner ring seal band
2304. the peripheral 2312. oilhole breach of oilhole 2305. oilhole 2306. oilhole 2307. oilhole 2308. oilhole 2308 oilhole 2310. guiding gutter 2311. oil distribution casing
24. floating ring
25 oil distribution mechanism butterfly springs
26. bonnet
27. protecgulum 2701. protecgulum left side
O1. cylinder cap spherical outside surface centre of sphere O2. the bearing holder (housing, cover) spherical outside surface centre of sphere
X. axis y. axis z. axis e. offset distance.
Detailed description of the invention
In order to make the technical characteristic of the present invention, purpose and beneficial effect become apparent from understanding, below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail.
As shown in Figure 8, a kind of middling speed high pulling torque radial plunger type motor, including housing 1, the bent axle 2 of external output speed and moment of torsion, it is arranged at housing 1 and the bearing 29 of protecgulum 27 endoporus, it is coated at the roller 3 of the eccentric shaft part 201 of bent axle 2, it is placed in the endoporus 401 of bearing holder (housing, cover) 4 in roller 3, the radially uniform cylinder cap 5 being anchored on housing 1 of star, along the extension sleeve 6 that bearing block 4 radial distribution and upper and lower side offset with the spherical outside surface 501 of cylinder cap 5 and the spherical outside surface 402 of bearing holder (housing, cover) 4 respectively, the lower end of extension sleeve 6 is close to all the time the retaining ring 7 of the spherical outside surface 402 of bearing holder (housing, cover) 4, the upper end of extension sleeve 6 is close to all the time the peg 8 of cylinder cap spherical outside surface 501, the power transmission shaft 10 that two ends are connected with bent axle 2 left end and oil distribution mechanism 9 respectively.
Extension sleeve 6 comprises oil cylinder 11 and 12 two parts of piston, oil cylinder 11 and piston 12 coaxial cooperation, and axis is z, and axis z is all the time by the centre of sphere O of the spherical outside surface 501 of cylinder cap 51Centre of sphere O with the spherical outside surface 402 of bearing holder (housing, cover) 42, during work, oil cylinder 11 and piston 12 are along the centre of sphere O of z-axis stretching motion and the sphere 501 around cylinder cap 51Swing.
Bent axle 2, roller 3, bearing holder (housing, cover) 4 constitute a rolling bearing structure, during work, slip between oil cylinder 11 with bearing holder (housing, cover) 4 is converted into the relative rolling between bearing holder (housing, cover) 4 and bent axle 2, be far smaller than the ultimate principle of force of sliding friction according to tribology force of rolling friction, described scheme is substantially improved the frictional behavior of described middling speed high pulling torque radial plunger type motor.
The spherical outside surface 402 of the Internal Spherical Surface 1101 of oil cylinder 11 with bearing holder (housing, cover) 4 is adjacent to by the circlip 15 being close to by retaining ring 7, retaining ring pressing plate 13, the elastic rubber ring 14 being arranged between retaining ring 7 and retaining ring pressing plate 13 and retaining ring pressing plate 13 and be fastened in bearing holder (housing, cover) 4 groove, and the face of being adjacent to seals.
Piston Internal Spherical Surface 1201 and cylinder cap spherical outside surface 501 being adjacent to by pallet 16, self-locking nut 17, peg 8, peg ring 18, butterfly spring 19, spring base 20, circlip 21, slipper seal effect is played in the face of being adjacent to.
nullOil distribution mechanism 9 includes oil-distributing plate 22、Oil distribution casing 23、Floating ring 24、Butterfly spring 25、Bonnet 26，Power transmission shaft 10 traverse housing 1 and oil-distributing plate 22 other end that one end is hinged with bent axle 3 are hinged with oil distribution casing 23，During work，Bent axle 2、Power transmission shaft 10、Oil distribution casing 23 synchronizes to rotate forward or backwards around axle x，Floating ring 24 is directly pressed on oil distribution casing 23 by one end and bonnet 26 butterfly spring 25 that the other end and floating ring 24 offset that offsets，And then indirectly oil distribution casing 23 is pressed on oil-distributing plate 22，Play initial sealing and wear-compensating effect，Namely after abrasion occurring between floating ring 24 and oil distribution casing 23 or between oil distribution casing 23 and oil-distributing plate 22，Under the elastic force effect of butterfly spring 25，Between floating ring 24 and oil distribution casing 23、Remain in that between oil distribution casing 23 and oil-distributing plate 22 and be adjacent to.
Described bearing block about 4 two ends offset with the step surface 101 of housing 1 and gap, protecgulum 27 left side 2701 respectively, namely bearing block 4 is retrained along the degree of freedom in axle y direction by described step surface 101 and described left side 2701, but bearing block 4 can rotate freely around axle x again together with bent axle 2.
During work, hydraulic oil is assigned to housing 1 and cylinder cap 5 runner successively through oil distribution structure 9, entering the cavity volume surrounded by cylinder cap 5, oil cylinder 11, piston 12, spheric seat 4, spheric seat 4 is produced thrust by the hydraulic pressure oil column that described cavity volume surrounds, and described thrust line passes through O all the time2, because of O2Have an offset distance e with the axis x of bent axle 2, so bent axle 2 is produced torque by described thrust, cause bent axle 2 to rotate around axis x, external output speed and moment of torsion, spheric seat 4 while axle x revolves round the sun around axle y rotation.
As the present embodiment technical scheme more specifically:
Such as Fig. 9, oil cylinder 11 is set to hollow and thin-walled column structure, and lower end (namely near Internal Spherical Surface 1101 one end) external diameter arranges a groove 1102, and for reducing motor axial dimension, the diameter A of groove 1102 is more smaller than oil cylinder internal diameter B, and A/B approximates 0.8～0.85；Considering the contact stress of the mechanical strength of oil cylinder 11 and the spherical outside surface 1101 of oil cylinder 11 and the spherical outside surface 402 of bearing block 4, the size C of oil cylinder 11 should be not too small, and C/A is no less than 0.5, it is preferred that 0.7～0.8 simultaneously.The purpose of design of above-mentioned oil cylinder 11 is to obtain minimum physical dimension under the premise ensureing mechanical strength, reduces movement inertia, and this is particularly important to improving motor rotary speed.
Because peg 8 spherical outside surface 802 and peg ring 18 Internal Spherical Surface 1801 are close to, for avoiding hydraulic oil to produce to impact to peg 8, as shown in Figure 10, peg 8 being opened some oil leak hole 803, the quantity of oil leak hole 803 and diameter depend on motor displacement size.
As shown in figure 11, eccentric shaft part 201 left end of bent axle 2 arranges one around the convex annular step 202 of axle y, positions use temporarily, do not play functional effect during work during for assembly or disassembly.Therefore, size L precision and step end face 203 fineness are all without too high requirement, and therefore Crankshaft Machining is convenient；Concentrate for reducing or eliminating stress, eccentric shaft part 201 arranges some roads compensating groove 204.
As shown in partial enlargement Figure 12, retaining ring 7 is fastened on the groove 1102 of oil cylinder 11 external diameter, retaining ring 7 is applied elastic force by the elastic rubber ring 14 being arranged between retaining ring 7 and retaining ring pressing plate 13, all the time retaining ring 7 is buckled on the groove 1102 of oil cylinder 11, the Internal Spherical Surface 1101 making oil cylinder 11 is adjacent to the spherical outside surface 402 of spheric seat 4 all the time, is adjacent in the face of the hydraulic oil of oil cylinder 11 hollow cavity applies to seal.Described elastic rubber ring 14 material is the nitrile rubber of oil resistant, and cross section can be circular, square, star or other shape.Compared with designing with the butterfly spring of prior art, can be embedded in because of elastic rubber ring 14 in retaining ring pressing plate 13 or retaining ring 7 groove, save installing space, size is more compact, it addition, elastic rubber ring also has the damping action absorbing energy, vibration and noise can be reduced to a certain extent.
With reference to Fig. 8,13,14, oil distribution casing 23 and oil-distributing plate 22 plane that offsets is provided with concentric outer ring seal band 2301, medium ring band 2302, inner ring seal band 2303.On described outer ring seal band 2301, outer interior interlocking is provided with two row's oilholes 2304 and 2305, often row's oilhole quantity can be 2,3,4 ..., specifically depending on motor displacement size and applying working condition, hydraulic oil on oil distribution casing 23 guiding gutter 2310 and peripheral 2311 enters each oilhole by the breach 2312 of each described oilhole, and friction pair is carried out forced feed lubrication.The external envelope radius of circle of described interior row's oilhole 2305 is bigger than the interior envelope radius of circle of described outer shroud oilhole 2304, i.e. R1> R2, its object is to floating ring 22 and oil distribution casing 23 outer ring seal band 2301 contact surface can be lubricated.Medium ring band 2302 and inner ring seal are identical with the oilhole method to set up on 2301 and purpose with the lubrication hydraulic fluid port method to set up on 2303 and purpose thereof and outer ring seal, and this no longer describes in detail.
Particular embodiments described above, is only preferred embodiment of the present invention, the equal design such as done according to the present patent application the scope of the claims, all should be the technology of the present invention and is contained.

Claims (21)

  1. null1. a middling speed high pulling torque radial plunger type motor，Including housing (1)、The bent axle (2) of external output speed and moment of torsion，It is coated at the roller (3) of the eccentric shaft part (201) of bent axle (2)、It is placed in roller (3) in the endoporus (401) of bearing holder (housing, cover) (4)、The radially uniform cylinder cap (5) being anchored on housing (1) of star、Along the extension sleeve (6) that bearing block (4) radial distribution and upper and lower side offset with the spherical outside surface (501) of cylinder cap (5) and the spherical outside surface (402) of bearing holder (housing, cover) (4) respectively、The lower end of extension sleeve (6) is close to all the time the retaining ring (7) of the spherical outside surface (402) of bearing holder (housing, cover) (4)、The upper end of extension sleeve (6) is close to all the time the peg (8) of cylinder cap spherical outside surface (501)、The power transmission shaft (10) that two ends are connected with bent axle (2) and oil distribution mechanism (9) respectively；
    Described extension sleeve (6) comprises oil cylinder (11) and piston (12), described oil cylinder (11) and described piston (12) coaxial cooperation, and axis (z) is all the time by the centre of sphere (O of the spherical outside surface (501) of cylinder cap (5)1) and the centre of sphere (O of spherical outside surface (402) of bearing holder (housing, cover) (4)2), during work, the centre of sphere (O of oil cylinder (11) and piston (12) edge (z) axle stretching motion and the sphere (501) around cylinder cap (5)1) swing；
    Described bent axle (2), roller (3), bearing holder (housing, cover) (4) constitute a rolling bearing structure；
    Also include retaining ring (7), retaining ring pressing plate (13), the elastic rubber ring (14) that is arranged between retaining ring (7) and retaining ring pressing plate (13), the circlip (15) being close to retaining ring pressing plate (13) and be fastened in described bearing holder (housing, cover) (4) groove, the spherical outside surface (402) of the Internal Spherical Surface (1101) of oil cylinder (11) Yu bearing holder (housing, cover) (4) is adjacent to by described circlip (15)；
    Also including pallet (16), self-locking nut (17), peg (8), peg ring (18), butterfly spring (19), spring base (20), circlip (21), piston Internal Spherical Surface (1201) and cylinder cap spherical outside surface (501) are adjacent to by described pallet (16), self-locking nut (17), peg (8), peg ring (18), butterfly spring (19), spring base (20), circlip (21)；
    nullAlso include oil distribution mechanism (9)，Described oil distribution mechanism (9) includes oil-distributing plate (22)、Oil distribution casing (23)、Floating ring (24)、Butterfly spring (25)、Bonnet (26)，Power transmission shaft (10) traverse housing (1) and oil-distributing plate (22) other end that one end is hinged with bent axle (3) are hinged with oil distribution casing (23)，During work，Bent axle (2)、Power transmission shaft (10)、Oil distribution casing (23) synchronizes (x) to rotate forward or backwards around axle，Floating ring (24) is directly pressed on oil distribution casing (23) by one end and bonnet (26) butterfly spring (25) that the other end and floating ring (24) offset that offsets，And then indirectly oil distribution casing (23) is pressed on oil-distributing plate (22)，Play initial sealing and wear-compensating effect，Namely after abrasion occurring between floating ring (24) and oil distribution casing (23) or between oil distribution casing (23) and oil-distributing plate (22)，Under the elastic force effect of butterfly spring (25)，Between floating ring (24) and oil distribution casing (23)、Remain in that between oil distribution casing (23) and oil-distributing plate (22) and be adjacent to；
    Described bearing holder (housing, cover) (4) two ends, left and right offset with the step surface (101) of housing (1) and protecgulum (27) left side (2701) gap respectively, namely bearing holder (housing, cover) (4) is retrained along the degree of freedom in axle (y) direction by described step surface (101) and described left side (2701), but bearing holder (housing, cover) (4) (x) can rotate freely around axle again together with bent axle (2).
  2. 2. middling speed high pulling torque radial plunger type motor according to claim 1, it is characterized in that: oil cylinder (11) is set to hollow and thin-walled column structure, the described oil cylinder (11) external diameter near Internal Spherical Surface (1101) one end arranges a groove (1102), and the diameter A of described groove (1102) is more smaller than oil cylinder internal diameter B.
  3. 3. middling speed high pulling torque radial plunger type motor according to claim 2, it is characterized in that: the ratio of the diameter A of described groove (1102) and oil cylinder internal diameter B approximates 0.8～0.85, the ratio of the truncated-spherical size C of oil cylinder (11) and the diameter A of groove (1102) is not less than 0.5.
  4. 4. middling speed high pulling torque radial plunger type motor according to claim 3, is characterized in that: the ratio of the truncated-spherical size C of described oil cylinder (11) and the diameter A of groove (1102) is 0.7～0.8.
  5. 5. middling speed high pulling torque radial plunger type motor according to claim 1, is characterized in that: described piston (12) is set to hollow and thin-walled column structure.
  6. 6. middling speed high pulling torque radial plunger type motor according to claim 1, is characterized in that: eccentric shaft part (201) left end of described bent axle (2) arranges one around the convex annular step (202) of axle (y).
  7. 7. middling speed high pulling torque radial plunger type motor according to claim 6, is characterized in that: the eccentric shaft part (201) of described bent axle (2) arranges 2-4 road compensating groove.
  8. 8. middling speed high pulling torque radial plunger type motor according to claim 1, is characterized in that: the endoporus (401) of described bearing holder (housing, cover) (4) is set to one without the unthreaded hole on boss rank.
  9. 9. middling speed high pulling torque radial plunger type motor according to claim 8, is characterized in that: the endoporus (401) of described bearing holder (housing, cover) (4) arranges 2 road compensating grooves.
  10. 10. middling speed high pulling torque radial plunger type motor according to claim 1, it is characterized in that: an elastic rubber ring (14) is set between described retaining ring (7) and retaining ring pressing plate (13) and places the groove of elastic rubber ring (14), groove both may be disposed in retaining ring (7), it is possible to is arranged on retaining ring pressing plate (13).
  11. 11. middling speed high pulling torque radial plunger type motor according to claim 10, it is characterized in that: elastic rubber ring (14) material being arranged between retaining ring (7) and retaining ring pressing plate (13) is nitrile rubber, elastic rubber ring (14) cross section can be circular, square, star or other shape.
  12. 12. middling speed high pulling torque radial plunger type motor according to claim 10, it is characterized in that: described retaining ring (7) arranges an endoporus, retaining ring pressing plate (13) arranges a boss, and the endoporus of retaining ring (7) coordinates with the boss of retaining ring pressing plate (13), and cooperation axis is axle (y).
  13. 13. middling speed high pulling torque radial plunger type motor according to claim 1, it is characterized in that: the periphery of described oil cylinder (11) lower end, namely offset with spheric seat (4) periphery of one end arranges a groove, retaining ring (7) is fastened on the groove that oil cylinder (11) lower end is peripheral, by retaining ring (7), it is arranged at the elastic rubber ring (14) between retaining ring (7) and retaining ring pressing plate (13), retaining ring pressing plate (13), the spherical outside surface (402) of the Internal Spherical Surface (1101) of oil cylinder (11) Yu bearing holder (housing, cover) (4) is adjacent to by the circlip (15) being close to retaining ring pressing plate (13) and be fastened in bearing holder (housing, cover) (4) groove.
  14. 14. middling speed high pulling torque radial plunger type motor according to claim 1, it is characterized in that: described piston (12) endoporus arranges a ring-shaped step (1202), by the pallet (16) offseted with ring-shaped step (1202), the self-locking nut (17) coordinated with the screw thread (801) of peg (8), peg (8), piston Internal Spherical Surface (1201) and cylinder cap spherical outside surface (501) are adjacent to by peg ring (18), butterfly spring (19), spring base (20), circlip (21).
  15. 15. middling speed high-torque hydraulic motor according to claim 14, it is characterized in that: described peg (8) and peg ring (18) are respectively provided with a spherical outside surface (802) and Internal Spherical Surface (1801), and two spheres (802) and (1801) offset, and can do relative sliding.
  16. 16. middling speed high pulling torque radial plunger type motor according to claim 15, it is characterized in that: described peg (8) arranges 2-4 oil through (803), size and the quantity basis motor displacement size in hole and determine.
  17. 17. middling speed high pulling torque radial plunger type motor according to claim 1, it is characterized in that: the centre of sphere (O of the spherical outside surface (501) of described cylinder cap (5)1) it is arranged on the outside of cylinder cap (5) entity.
  18. 18. middling speed high pulling torque radial plunger type motor according to claim 1, it is characterized in that: described cylinder cap (5), peg (8), peg ring (18), the sphere (501) of (12) four parts of piston, (802), (1801), (1201) the centre of sphere concentric.
  19. 19. middling speed high pulling torque radial plunger type motor according to claim 1, it is characterized in that: described oil distribution casing (23) and described oil-distributing plate (22) plane that offsets is provided with three concentric ring bands, it is outer ring seal band (2301) respectively, medium ring band (2302), inner ring seal band (2303), described outer ring seal band (2301) upper outer interior interlocking is provided with two row's oilhole (2304) and (2305), often row's oilhole quantity is 2 or more than 2, the external envelope radius of circle of described interior row's oilhole (2305) is bigger than the interior envelope radius of circle of described outer shroud oilhole (2304), i.e. R1> R2。
  20. 20. middling speed high pulling torque radial plunger type motor according to claim 19, it is characterized in that: described medium ring band (2302) upper outer interior interlocking is provided with two row's oilhole (2306) and (2307), often row's oilhole quantity is 2 or more than 2, the external envelope radius of circle of described interior row's oilhole (2307) is bigger than the interior envelope radius of circle of described outer shroud oilhole (2306), i.e. R3> R4。
  21. 21. middling speed high pulling torque radial plunger type motor according to claim 19, it is characterized in that: described inner ring seal band (2303) upper outer interior interlocking is provided with two row's oilhole (2308) and (2309), often row's oilhole quantity is 2 or more than 2, the external envelope radius of circle of described interior row's oilhole (2309) is bigger than the interior envelope radius of circle of described outer shroud oilhole (2308), i.e. R5 > R6.
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CN106523263A (en) * 2016-12-27 2017-03-22 宁波欧易液压有限公司 Tilt cylinder type hydraulic motor
WO2017181907A1 (en) * 2016-04-19 2017-10-26 佛山市顺德区中意液压有限公司 Medium-speed high-torque radial piston hydraulic motor
CN108506273A (en) * 2018-06-13 2018-09-07 山东大学 A kind of commutation type hydraulic motor
CN109975028A (en) * 2019-04-11 2019-07-05 佛山市顺德区中意液压有限公司 Radial plunger piston motor oil cylinder eccentric shaft friction friction force measuring device and its measurement method
CN110410268A (en) * 2019-07-21 2019-11-05 杭州电子科技大学 A kind of rotating flow distribution motor

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CN108506273A (en) * 2018-06-13 2018-09-07 山东大学 A kind of commutation type hydraulic motor
CN108506273B (en) * 2018-06-13 2024-01-19 山东大学 Reversing hydraulic motor
CN109975028A (en) * 2019-04-11 2019-07-05 佛山市顺德区中意液压有限公司 Radial plunger piston motor oil cylinder eccentric shaft friction friction force measuring device and its measurement method
CN110410268A (en) * 2019-07-21 2019-11-05 杭州电子科技大学 A kind of rotating flow distribution motor

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