CN202091108U - Bevel board type hydraulic machinery and static oil pressure driving device - Google Patents
Bevel board type hydraulic machinery and static oil pressure driving device Download PDFInfo
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- CN202091108U CN202091108U CN2011201558411U CN201120155841U CN202091108U CN 202091108 U CN202091108 U CN 202091108U CN 2011201558411 U CN2011201558411 U CN 2011201558411U CN 201120155841 U CN201120155841 U CN 201120155841U CN 202091108 U CN202091108 U CN 202091108U
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- 238000000034 method Methods 0.000 claims description 31
- 230000008569 process Effects 0.000 claims description 30
- 230000015572 biosynthetic process Effects 0.000 claims description 28
- 230000005540 biological transmission Effects 0.000 claims description 6
- 230000002093 peripheral effect Effects 0.000 abstract description 7
- 239000000446 fuel Substances 0.000 description 17
- 230000009471 action Effects 0.000 description 14
- 230000008859 change Effects 0.000 description 13
- 230000014509 gene expression Effects 0.000 description 13
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical compound C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 description 13
- 238000012795 verification Methods 0.000 description 8
- 230000007935 neutral effect Effects 0.000 description 6
- 238000009434 installation Methods 0.000 description 5
- 238000006243 chemical reaction Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
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- 230000004323 axial length Effects 0.000 description 2
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- 230000001133 acceleration Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
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Abstract
An oil pressure pump (12) and an oil pressure motor taken as bevel board type hydraulic machinery comprise a drive shaft (16) which is in key embedded with an oil pressure cylinder body (68) by a convex spline (88). The drive shaft (16) comprises a second convex spline (90), i.e. a boss disposed on the peripheral surface which is depart from the part of the convex spline (88) along with the axial direction. When a housing (34) and a port seat are assembled with each other in a separating way, the second convex spline (90) can be contacted with the cylinder body (68) along with the peripheral direction, and the relative position between the cylinder body (68) and the drive shaft (16) along with a rotating direction is maintained regardless of the elastic force applied to a spring (72). The second convex spline (90) can not be contacted with the cylinder body (68) under the condition that the housing (34) has been combined with the port seat.
Description
Technical field
The utility model relates to ramp type hydraulic machinery and quiet oil hydraulic actuator, have mowing machine or tiller etc. over the ground working machine vehicle or have in the traveling gear of mechanically moving etc. of excavators such as backhoe, under situation with running parts such as hydraulic motor driving wheel or crawler belts, this ramp type hydraulic machinery and quiet oil hydraulic actuator are used as hydraulic motor or oil pressure pump, perhaps the oil pressure pump that stretches with the oil hydraulic cylinder device as the arm that makes excavator.For example, the ramp type hydraulic machinery is used as and has movable swash plate or the fixedly oil pressure pump or the hydraulic motor of swash plate.Quiet oil hydraulic actuator possesses oil pressure pump and by supplying with the hydraulic motor that the pressure oil spue from oil pressure pump drives, carries out quiet hydraulic transmission with oil pressure pump and hydraulic motor.
Background technique
In the past, for example used the traveling gear of above-mentioned running parts such as hydraulic motor driving wheel known.That is, this traveling gear possesses the driving source of hydraulic motor as its running part.And, for the Pressure oil feeder hydraulic motor, in traveling gear, be provided with motor or electric motor driven oil pressure pump.
The closed-loop path is made in the oil hydraulic circuit that comprises hydraulic motor and oil pressure pump, will become the suction port of hydraulic motor and discharge opening the two one of 2 ports be communicated to respectively on 2 ports of oil pressure pump.According to such formation, for example, oil pressure pump or hydraulic motor are made movable ramp type hydraulic machinery, by change movable swash plate to the inclination corner of live axle for oppositely, just can switch rotating and reverse of hydraulic motor.
Drive the oil hydraulic pump that records in the flat 10-169547 communique as the ramp type hydraulic machinery Japanese Patent Application Publication document spy.This oil hydraulic pump is rotatably supported in inside corresponding to the housing of shell to live axle, the cylinder body that is arranged on enclosure interior is combined on the live axle with spline again.Can reciprocatingly dispose piston in a plurality of cylinders chamber of cylinder body, the globular part that will be formed on an end of each piston through crawler shoe pushes up to swash plate.Outer circumferential face pushes up the spherical shape pad to the swash plate side with the spring via pins between the outer circumferential face of the inner peripheral surface that is arranged on cylinder body and live axle, again by pad the crawler shoe roof pressure on swash plate.The face in the face of cylinder body of housing is provided with valve plate, and valve plate can slip with the end face of cylinder body.The hole in the face of the induction stroke that is formed with the division fluid on the pitch circle in cylinder chamber and the stroke that spues of valve plate.
According to such oil hydraulic pump, an end of each piston rotates along swash plate through crawler shoe, and each piston is with regard to to-and-fro motion.And, corresponding to moving forward and backward of piston, divide spuing and sucking of fluid by valve plate.As the relevant prior art document of the utility model, except that Japanese Patent Application Publication document spy opens flat 10-169547 communique, also have the Japanese Patent Application Publication document to open flat 5-50079 communique in fact.
Yet, under the situation of the oil hydraulic pump of in Japanese kokai publication hei 10-169547 communique, putting down in writing, owing between the outer circumferential face of the inner peripheral surface of cylinder body and live axle, be provided with spring, so increase the radial dimension of cylinder body easily.On the other hand, all the time, in order to make the ramp type hydraulic machinery high capacity of oil hydraulic pump etc., people do the quantity in cylinder chamber or the volume in each cylinder chamber greatly considering again.In the pump of in Japanese kokai publication hei 10-169547 communique, putting down in writing, needing under the situation of high capacity, further increase the radial dimension of cylinder body, be unfavorable for the miniaturization of ramp type hydraulic machinery.Therefore, people consider to omit the spring between the outer circumferential face of the inner peripheral surface of cylinder body and live axle, and spring is arranged on the inside in a plurality of cylinders chamber, with these springs through piston the crawler shoe roof pressure on swash plate.
For example, real opening records a kind of ramp type hydraulic machinery in the flat 5-50079 communique in Japan, promptly as the axial piston pump of oil pressure pump.This axial piston pump live axle at shell with corresponding to the end caps rotatably support of the cylinder body of band edge mouth.With the spline connecting part cylinder body is combined in the outer circumferential side of live axle, on cylinder body, is formed with a plurality of cylinders chamber, but disposes piston in each cylinder chamber axial displacement.The spring that is arranged in each cylinder chamber imposes the elastic force that is provided with the forward end in spherical piston bulb towards it to piston, and the piston bulb is slipped on crawler shoe.Make on the intersection point that the center line of face that the central position of spline connecting part is formed on the central position by each piston bulb and live axle intersects.Switch to when spuing stroke from induction stroke at piston, pressure in the cylinder chamber sharply rises, swash plate reaction force W0 is added on the auxiliary section of piston bulb and crawler shoe from swash plate, and the component W2 of the swash plate reaction force direction with orthogonal axe live axle W0 puts on the spline connecting part.But, as mentioned above,,, do not grind partially thereby on the spline connecting part, can not produce so component W0 puts on the whole spline connecting part equably owing to define the central position of spline connecting part.
, under situation about as described above spring being arranged in each cylinder chamber, the assembling work of pump might be very difficult.That is: when the assembling of pump, under the state that shell and end cap are separated, make live axle by the inboard of spline fitted at cylinder body so that drive shaft bearing in the enclosure in, cylinder body is configured in the inboard of shell.But in such cases, the spring that is arranged in each cylinder chamber is elongated to its free length, might become cylinder body is projected into the outside from the opening end of shell state.Therefore, after this must overcome end cap that the elastic force of each spring will become lid in cylinder body is pressed into shell, again end cap is combined on the shell.But, at cylinder body from shell under the outstanding state, the positive spline that constitutes the live axle of spline connecting part breaks away from the cloudy spline of cylinder body and cooperates, in case both teeth phase shiftings, only axially push end cap along live axle, two splines are combined, and are difficult to make its phase place as one man two splines to be combined and shell is combined with end cap.
In the superincumbent description, illustrated that the ramp type hydraulic machinery is the situation of oil hydraulic pump, even but the ramp type hydraulic machinery is the situation of oil hydraulic motor, also might produce same drawback.To make common single shell as the shell of the oil pressure pump of ramp type hydraulic machinery and the shell of hydraulic motor, and carry out with oil pressure pump and hydraulic motor also might producing and above-mentioned same drawback under the situation of quiet oil hydraulic actuator of quiet hydraulic transmission.
Summary of the invention
The purpose of this utility model is not increase the radial dimension of cylinder body in ramp type hydraulic machinery and quiet oil hydraulic actuator, and in reaching the formation of high power capacity, realizes the facilitation of assembling work.
Ramp type hydraulic machinery of the present utility model possesses shell, be combined in the member of the band edge mouth on the described shell separably, be supported on the member of described shell and described band edge mouth and comprise the live axle that is arranged on the spline part on the outer circumferential face, be engaged on the described live axle and rotate integratedly with described live axle and slip cylinder body on the member of described band edge mouth by described spline part, but be configured in to to-and-fro motion a plurality of pistons in a plurality of cylinders chamber that is formed on the described cylinder body, be arranged on a plurality of springs between described each cylinder chamber and described each piston, and be supported in the described shell and comprise the swash plate of the plane of inclination that described relatively in use live axle tilts; The head of described piston is followed the rotation of described cylinder body and slide in the plane of inclination of described relatively swash plate, thereby makes described reciprocating motion of the pistons; Described live axle comprises the projection on the outer circumferential face that is arranged on the part of leaving described spline part vertically; Under state in the cylinder body is separated and a plurality of pistons and spring be assembled to the member of described shell and described band edge mouth, under the situation of drive shaft bearing in described shell that is inserted in the described cylinder body, just in assembly process, what described projection can be along described live axle circumferentially or axially contacts described cylinder body; To by the elastic force of described spring when the spline part of described live axle is released, keep described cylinder body and the relative position of described live axle on sense of rotation at described cylinder body; Under the situation of the member combination of described shell and described band edge mouth, described projection does not contact with described cylinder body.
In ramp type hydraulic machinery of the present utility model, described projection preferably has and the roughly the same external diameter of external diameter that is formed on the key tooth on the described spline part.
In ramp type hydraulic machinery of the present utility model, described projection preferably comprises second spline tooth, and the phase place of the key tooth on making it and being formed on described spline part is consistent; Limit the position of described projection with respect to described live axle, so that in described assembly process, described spring is in described cylinder body under the situation of free length, and described cylinder body is positioned on the described projection, and is maintained described cylinder body and the relative position of described live axle on sense of rotation.
In ramp type hydraulic machinery of the present utility model, described projection preferably has the contacting part that can contact described cylinder body in described assembly process vertically; Limit the position of described projection with respect to described live axle, so that in described assembly process, the moving axially of the described cylinder body of described protrusions limit, thus it is chimeric to be maintained the key that described cylinder body and described live axle realized by described spline part.
Quiet oil hydraulic actuator of the present utility model possesses oil pressure pump and is supplied to the compressed oil that spues from described oil pressure pump and the hydraulic motor that drives carried out quiet hydraulic transmission by described oil pressure pump and described hydraulic motor; One of described oil pressure pump and described hydraulic motor side or two sides are made of ramp type hydraulic machinery of the present utility model; Constituting the shell of described oil pressure pump and the shell of the described hydraulic motor of formation is made of a common shell; Constituting the member of band edge mouth of described oil pressure pump and the member that constitutes the band edge mouth of described hydraulic motor is made of the member of a common band edge mouth.
According to ramp type hydraulic machinery of the present utility model and quiet oil hydraulic actuator, do not increase the radial dimension of cylinder body and can reach high power capacity, in assembly process, even because of the elastic force of the spring in the cylinder chamber makes cylinder body under the outstanding situation of the opening end of shell, constitute the also non-migration of phase place of sense of rotation of the cloudy spline of the positive spline of live axle of spline embedding part and cylinder body.Therefore, can easily carry out operation, and realize the facilitation of assembling work in conjunction with the member of shell and band edge mouth.
Description of drawings
Fig. 1 is the diagrammatic sketch that comprises the oil hydraulic circuit of the routine quiet oil hydraulic actuator of one of mode of execution of the present utility model.
Fig. 2 is the sectional view of the concrete example of the routine quiet oil hydraulic actuator of one of expression mode of execution of the present utility model.
Fig. 3 is the A-A sectional view of Fig. 2.
Fig. 4 is a view of seeing the oil feed pump standing part of Fig. 2 from the right side to the left.
Fig. 5 is the B-B sectional view of Fig. 4.
Fig. 6 is the diagrammatic sketch of one of the situation example of the expression installation direction that changed oil feed pump, corresponding to Fig. 4.
Fig. 7 is other routine sectional views of piston shoe of the quiet oil hydraulic actuator of expression pie graph 2.
Fig. 8 be in the assembly process of separating on the member of band edge mouth and the shell state down expression comprise the sectional view of part of pump important document of the upside of Fig. 2.
Fig. 9 be in the assembly process of separating on the member of band edge mouth and the shell state down expression comprise the sectional view of part of motor important document of the downside of Fig. 2.
Figure 10 is in the quiet oil hydraulic actuator of another example of mode of execution of the present utility model, and expression is corresponding to the sectional view of the part that comprises the motor important document of Fig. 2.
Figure 11 be in the assembly process of separating on the member of band edge mouth in the formation of Figure 10 and the shell state down expression comprise the sectional view of the part of motor important document.
Figure 12 separates the sectional view of expression with a plurality of important documents in the formation of Figure 11.
Embodiment
Below describe in detail with accompanying drawing and to relate to mode of execution of the present utility model.What Fig. 1 represented to Fig. 9 is one of mode of execution of the present utility model example.At first, comprise the oil hydraulic circuit of the quiet oil hydraulic actuator of present embodiment with Fig. 1 explanation.At the vehicle of the working machine over the ground that for example has mowing machine or tiller etc. or have in the traveling gear of mechanically moving etc. of excavators such as backhoe the running part of quiet oil hydraulic actuator 10 usefulness cause hydraulic motor driving wheel shown in Fig. 1 or crawler belt etc.Following description line walking apparatus is a vehicle and running part is the situation of wheel.Quiet oil hydraulic actuator 10 possesses oil pressure pump 12 and hydraulic motor 14, and hydraulic motor 14 is supplied to the oily compressed oil of conduct action that spues from oil pressure pump 12 and drives.Quiet oil hydraulic actuator 10 usefulness oil pressure pumps 12 and hydraulic motor 14 carry out quiet hydraulic transmission.
That is to say that it is pump side first port P1 and the pump side second port P2 that oil pressure pump 12 has two ports; It is motor-side first port M1 and the motor-side second port M2 that hydraulic motor 14 has two ports.The first oil circuit S1 connects the first port P1, the M1 of oil pressure pump 12 and hydraulic motor 14 respectively, and the second oil circuit S2 connects the second port P2, the M2 of oil pressure pump 12 and hydraulic motor 14 respectively.The first oil circuit S1 and the second oil circuit S2 combine oil pressure pump 12 and hydraulic motor 14 and constitute the fluid dynamic major loop.
Oil pressure pump 12 is that the variable displacement pump with movable swash plate is the ramp type hydraulic machinery, but is attached to the rotating live axle 16 on the driving source E such as motor or motor with possessing transferring power.Is service pump that the rotors such as internal rotor of oil feed pump 18 are attached on the live axle 16, just can drive oil feed pump 18 by the driving of live axle 16.The driving of live axle 16 will add the action oil that presses and spue from one of the first port P1 and second port P2 square end mouth, and from the opposing party's port suction action oil.Oil pressure pump 12 can change movable swash plate with the supporting of movable swash plate in the enclosure to the angle of inclination of live axle 16 corner that promptly tilts.
Be provided with in the enclosure swash plate service axis rotate just can change movable swash plate towards and angle.Movable swash plate towards determining exhaust end and the suction side of the first port P1 and the second port P2 with angle, the also decision capacity that spues.Acceleration instruction unit corresponding to the driver's seat periphery that is arranged on vehicle is the operation of speed change lever 20, and suitable power source or power transfering part are given the swash plate service axis with power, and the swash plate service axis rotates.
The first pedestal port PA opening is the outer surface of port seat 36 (Fig. 2) at the member of the band edge mouth that constitutes quiet oil hydraulic actuator 10, and exhaust end pump port PB is arranged on the oil feed pump 18 that is fixed in the shell 34 (Fig. 2) that constitutes quiet oil hydraulic actuator 10.Pipe arrangement 24 is connected on these two port PA, PB, pipe arrangement 24 be provided with in-line filter F midway.In the inside of port seat 36, the first pedestal port PA is connected between the replenishing relief valve 26 and a pair of fuel feeding certificated valve 28,30 that constitutes oil supply loop SC respectively.Replenishing relief valve 26 has the function that the oil pressure in the oil supply loop SC is limited to the oil pressure below the setting value.The draining side of replenishing relief valve 26 is connected to space in the shell 34.The pressure that is lower than oil supply loop SC when the oil pressure of the first oil circuit S1 that becomes low voltage side or the second oil circuit S2 is fuel feeding when pressing, and primary side becomes the fuel feeding certificated valve 28 (or 30) of low voltage side opens, and oil supply loop SC is communicated to the first oil circuit S1 or the second oil circuit S2.Fuel feeding certificated valve 28,30 has the function of high-pressure safety valve, reach the above high pressure of setting value and open because of becoming the on high-tension side first oil circuit S1 or the second oil circuit S2, primary side becomes fuel feeding certificated valve 30 (or 28) unlatching of low voltage side simultaneously, and the residue oil pressure is added to the second oil circuit S2 or the first oil circuit S1 that becomes low voltage side.
With the outer surface of the second pedestal port PC opening at the shell 34 (Fig. 2) that constitutes quiet oil hydraulic actuator 10, pump port PD is arranged on the above-mentioned oil feed pump 18 the suction side, and these two port PC, PD are connected on the oil tank T.Be filled with oil in the space in shell 34, owing to the slide parts such as slide part of oil from piston and cylinder chamber spills, the oil that overflows just is discharged into the oil tank T from the second pedestal port PC.The driving of oil feed pump 18 just is drawn into oil in the oil feed pump 18 through suction side pump port PD from oil tank T, after the pressurization, spues from above-mentioned exhaust end pump port PB.
Be provided with throttle valve 32 in the fuel feeding certificated valve 30 in a pair of fuel feeding certificated valve 28,30, become the on high-tension side second oil circuit S2 side when vehicle advances, throttle valve 32 is being communicated with between a pair of fuel feeding certificated valve 28,30 among the second oil circuit S2 and the oil supply loop SC all the time.Therefore, when vehicle rollback, the action oil of high pressure passes through throttle valve 32 from the second oil circuit S2, and drain to oil supply loop SC side, but so in the operating range of speed change lever 20, can be easily be that the neutral width W of neutral state is set at certain size arbitrarily becoming neutral condition that hydraulic motor 14 do not rotate, rather than a bit.As shown in Figure 1, during vehicle rollback, escape to oil supply loop SC side from the second oil circuit S2 through throttle valve 32, will produce oil consumption in case action is oily, but owing to the situation execution frequency that retreats than advancing lacks, so practical no problem.
The concrete structure of the quiet oil hydraulic actuator 10 of present embodiment is described to Fig. 9 with Fig. 2 then.Quiet oil hydraulic actuator 10 has above-mentioned oil channel structures shown in Figure 1.In the following description, the key element same, mark prosign with key element shown in Figure 1.As shown in Figure 2, quiet oil hydraulic actuator 10 comprises respectively oil pressure pump 12 and the hydraulic motor 14 as the ramp type hydraulic machinery.That is, to possess the member of shell 34, band edge mouth be port seat 36, pump important document 38, motor important document 40 and oil feed pump 18 to quiet oil hydraulic actuator 10.Shell 34 and port seat 36, pump important document 38 constitute oil pressure pump 12; Shell 34 and port seat 36, motor important document 40 constitute hydraulic motor 14.That is to say, constitute the shell of oil pressure pump 12 and the shell of formation hydraulic motor 14 and constitute by a common shell 34.Constituting the port seat of oil pressure pump 12 and the port seat of formation hydraulic motor 14 is made of a common port seat 36.
Next, describe oil pressure pump 12 in detail.Oil pressure pump 12 possesses shell 34 and port seat 36, and shell 34 has living space 42 in the inboard, space 42 one-sided openings, and the joint that port seat 36 usefulness comprise bolt is combined on the shell 34 separably.Port seat 36 roughly constitutes tabular, effect with end cap of the opening that clogs shell 34, port seat 36 comprise makes the first pedestal port PA opening be bearing in pump valve plate 46 and motor valve plate 48 on the inner side surface (right side of Fig. 2) of pedestal main body 44 in the pedestal main body 44 of its outer surface, for the dislocation that prevents the face direction.Pump valve plate 46 has both sides that connect direction in the table of Fig. 2 (promptly perpendicular to Fig. 2 paper direction) respectively and pump side first port P1 (Fig. 1) and the pump side second port P2 (Fig. 1) that slightly is circular arc respectively.The first port P1 leads on the first oil circuit S1 shown in Figure 3, and the second port P2 leads on the second oil circuit S2 (Fig. 3).The back will describe motor valve plate 48 in detail.
As shown in Figure 3, in the horizontal passageway 50 that intersects with the first oil circuit S1 and the second oil circuit S2, dispose a pair of fuel feeding certificated valve 28,30 that has the safety valve function.Each fuel feeding certificated valve 28,30 has the 56 pairs of verification valve bodies 52 of first spring, 56, the first springs that are arranged on verification valve body 52 and are fixed between the stopper 54 on the port seat 36 and gives elastic force, makes its valve seat surface throttle down towards port seat 36.Be screwed in the head that is provided with 62 pairs of Safety valve bodies 58 of second spring, 62, the second springs between the retaining 60 of outer end of Safety valve body 58 and the verification valve body 52 and give elastic force, make its valve seat surface throttle down towards verification valve body 52.
In the fuel feeding certificated valve 28 of the first oil circuit S1 side, the first oil circuit S1 is led in the space that the Safety valve body 58 and second spring 62 cross; In the fuel feeding certificated valve 30 of the second oil circuit S2 side, the second oil circuit S2 is led in the space that the Safety valve body 58 and second spring 62 cross.In port seat 36, the horizontal passageway 64 between a pair of fuel feeding certificated valve 28,30 is being communicated with the oil circuit 66 that constitutes oil supply loop SC.Low voltage side in the first oil circuit S1 and the second oil circuit S2, the verification valve body 52 that constitutes fuel feeding certificated valve 28 (or 30) are lifted off a seat face and when opening, the oil circuit 66 of oil supply loop SC is connected to oil circuit S1 (or S2).Oil circuit 66 is being communicated with the first pedestal port PA of opening on first G1 of the outer circumferential face that constitutes port seat 36.Can be connected with the pipe arrangement (not shown) on the exhaust end pump port PB (Fig. 5) that leads to oil feed pump 18 (Fig. 5) on the first pedestal port PA.
In addition, impose elastic force, so that clog shell 34 side openings of oil circuit 66 by the valve body of the replenishing relief valve 26 (Fig. 2) that is arranged on shell 34 inboards with spring.The second pedestal port PC (Fig. 2) is connected to the outer surface of shell 34, and the second pedestal port PC is communicated in the space 42.Can be connected to the pipe arrangement 24 (Fig. 1) that leads to oil tank T (with reference to Fig. 1) on the second pedestal port PC.
As shown in Figure 3, the part by the center of verification valve body 52 that constitutes the fuel feeding certificated valve 30 of the second oil circuit S2 side in a pair of fuel feeding certificated valve 28,30 is provided with the throttle valve 32 of axial perforation.In fuel feeding certificated valve 30 sides, when Safety valve body 58 leans on the valve seat surface of verification valve body 52, verification valve body 52 leans on the valve seat surface of port seat 36 valve closing, even in this case, the oil circuit 66 of the second oil circuit S2 and oil supply loop SC is being communicated with through throttle valve 32.Therefore, as above-mentioned illustrated in fig. 1, but in the operating range of speed change lever 20, can be easily be that the neutral width of neutral state is set at certain size arbitrarily becoming neutral condition that hydraulic motor 14 do not rotate, rather than a bit.
As shown in Figure 2, oil pressure pump 12 possess with bearing be rotatably supported in live axle 16 on shell 34 and the port seat 36, by spline fitted on live axle 16 and can with cylinder body 68, a plurality of piston 70, a plurality of spring 72, movable swash plate 74 and a plurality of lining 76 of live axle 16 unitary rotation.Live axle 16 crosses space 42, and one end (left part of Fig. 2) is outstanding from the outer surface of port seat 36, can be directly or connect driving source E such as motor or electric motor through power transmission mechanism.The other end of live axle 16 (right part of Fig. 2) is outstanding from the outer surface of shell 34, is fixing the internal rotor 78 of oil feed pump 18.That is to say that oil feed pump 18 is the trochoid pumps that are provided with internal rotor 78 and external rotor in the inboard of pump case 80, is fixing internal rotor 78 in the end of live axle 16.
As Fig. 4, shown in Figure 5, pump case 80 is fastened on the outer side surface of shell 34 with a plurality of bolts 82.As shown in Figure 5, being provided with exhaust end pump port PB and suction side pump port PD in two places of opposition side radially, the inboard of each port PB, PD is communicated in the space that is provided with internal rotor 78 and external rotor with respect to the central axis of pump case 80.On exhaust end pump port PB, the pipe arrangement 24 (Fig. 1) that communicates with the first pedestal port PA (Fig. 2) can be connected, on the pump port PD of suction side, the pipe arrangement that communicates with oil tank T (Fig. 1) can be connected.Drive such oil feed pump 18 with live axle 16, the action oil after pressurizeing is supplied to oil supply loop SC from oil tank T.Oil feed pump 18 is not defined to such trochoid pump, can use various forms of pumps.
As Fig. 4, shown in Figure 5, shell 34 in the face of the outer surface of oil feed pump 18, be on the same pitch circle at center and phase place differs 4 places of 90 ° successively and is formed with pin hole 84 being positioned at the axle consistent with the central shaft of oil feed pump 18.Pump case 80 in the face of on the inner face of shell 34, supporting a locating stud 86 (Fig. 2) that can agree with each pin hole 84, its part is outstanding from the inner face of pump case 80.In the example of Fig. 4, the pin hole 84 that is arranged in Fig. 4 lower end that locating stud 86 is inserted in each pin hole 84 is located.Under this state, pump case 80 is fixed on the shell 34 with bolt 82.In Fig. 4 and Fig. 6 described later, for the purpose of understanding, represent locating stud 86 with X.Among Fig. 4, on the outer surface of shell 34, on the position of staggering with pin hole 84 on the same pitch circle that with the axle consistent with the central shaft of oil feed pump 18 is the center, phase place differs 4 local tapped holes that form of 90 ° successively, and bolt 82 is combined in each tapped hole.Therefore, the installment state of oil feed pump can be switched in one of four states.
For example, in Fig. 4, on the pump case 80 of oil feed pump 18,, be arranged on and comprise from the left and right sides of the above-below direction central part of Fig. 4 towards the inboard of the part of the outstanding a pair of teat of left and right directions suction side pump port PD and exhaust end pump port PB.On the outer side surface of pump case 80, inwardly arrow is indicated on the part that the inboard is provided with suction side pump port PD; On the outer side surface of pump case 80, outwardly arrow is indicated on the part that the inboard is provided with exhaust end pump port PB.Just can prevent the mistake dress of pipe arrangement with such sign to each pump port PD, PB.
With respect to this, Fig. 6 is corresponding to Fig. 4, and one of the situation example of the installation direction of oil feed pump has been changed in expression.Among Fig. 6, compare, make the installation direction of oil feed pump 18 be offset 90 degree with the situation of Fig. 4.That is: locating stud 86 is inserted a pin hole 84 of the left end that is positioned at Fig. 6 in each pin hole 84 of the outer surface that is formed on shell 34, locate thus.Under this state, with bolt 82 pump case 80 is fixed on the shell 34 again.In this case, in pump case 80, suction side pump port PD and exhaust end pump port PB are arranged on the inboard that comprises from the part of a pair of teat that direction is outstanding up and down of bi-side up and down of the left and right directions central part of Fig. 6.So, the installation direction of change oil feed pump 18 under 4 kinds of states so change installation direction according to the configuration status of the pipe arrangement that is connected to pump port PD, PB, can be realized the facilitation of the connection operation of pipe arrangement arbitrarily.And improved the degrees of freedom of handling pipe arrangement.
As shown in Figure 2, be provided with positive spline 88 in the axial intermediate portion of live axle 16 as spline part.Live axle 16 comprises the second positive spline 90, and this second positive spline 90 is arranged on the part promptly on the live axle outer circumferential face than the part of more close vertically port seat 36 sides of positive spline 88 of leaving positive spline 88 vertically.The second positive spline 90 is projections, and its axial length is less than positive spline 88.The back will describe the second positive spline 90 in detail.
But in each cylinder chamber 94, dispose to to-and-fro motion piston 70.As shown in Figure 8, but piston 70 be arranged on the piston main body 96 of the tubular in each cylinder chamber 94 with comprising to-and-fro motion and be supported on piston shoe 98 on the piston main body 96.Piston shoe 98 is heads of piston 70.Be provided with lining 76 in the inboard of each piston main body 96, lining 76 has the oilhole 100 that connects vertically at central part, and an axial end (right part of Fig. 8) of lining is provided with flange.Be provided with spring 72 between the flange of each lining 76 of the inboard of the inboard in each cylinder chamber 94 and piston main body 96 configuration, 72 pairs of pistons of spring 70 are given elastic force along the direction of releasing from cylinder body 68.That is: quiet oil hydraulic actuator 10 possesses a plurality of springs 72 that are arranged between each cylinder chamber 94 and each piston 70.
Front end (right part of Fig. 2) rotatably support at each piston main body 96 piston shoe 98.The outer circumferential face that this piston shoe 98 has a front end that is used for being bearing in this piston main body 96 is the globular part 102 of spherical shape and is wholely set slightly be discoideus roof pressure portion 104 on globular part 102 one-sided.Roof pressure portion 104 will be plane single face roof pressure on movable swash plate 74.Oilhole 106 is formed in globular part 102 and the roof pressure portion 104, and they are connected.No matter whether piston shoe 98 rotates relative to piston main body 96, be oil pressure hole 108 via the oilhole 100 that is formed on the lining 76 with the recess that the oilhole 106 that is formed on the piston shoe 98 is communicated on the single face that is arranged on roof pressure portion 104 all the time all in the cylinder chamber 94.Lining 76 is configured to such an extent that can and relatively rotate in the inboard displacement of piston main body 96.That is: the external diameter of the flange of lining 76 is less than the internal diameter of piston main body 96.
As shown in Figure 2, movable swash plate 74 is configured in the space 42 of inboard of shell 34.In shell 34, supporting sloping shaft (not shown) along direction in the table of Fig. 2, but supporting movable swash plate 74 to such an extent that opposite shell 34 is that rotate at the center with the sloping shaft.It is that rotate at the center with the sloping shaft that rotation makes movable swash plate 74 from the outstanding swash plate service axis 110 (Fig. 4, Fig. 6) of the outer surface of shell 34.Movable swash plate 74 expressions shown in the solid line of Fig. 2 turn to state to greatest extent along the clockwise direction of Fig. 2, and movable swash plate 74 expressions shown in the two point dotted line of Fig. 2 turn to state to greatest extent along the counter clockwise direction of Fig. 2.Corresponding to the operation of speed change lever 20 (Fig. 1), suitable power source or power transfering part are given swash plate service axis 110 with power, and swash plate service axis 110 rotates.The plane of inclination 112 that tilts with respect to live axle 16 when movable swash plate 74 comprises use.Roof pressure portion 104 roof pressures of piston shoe 98 (Fig. 8) are on plane of inclination 112.
Because the oil pressure that the action oil in the cylinder chamber 94 is fed in the roof pressure portion 104 that is arranged on piston shoe 98 is cheated in 108 (Fig. 8), so roof pressure portion 104 is indexed to the direction that plane of inclination 112 is lifted a little.Therefore, can prevent piston shoe 98 and the movably excessive wear between the swash plate 74.Fig. 2 makes simple rectangle to the section configuration that is arranged on the oil pressure hole 108 in the roof pressure portion 104 in the formation of Fig. 6, Fig. 8.But, also can change the shape in this oil pressure hole 108.Fig. 7 is the sectional view of other examples of piston shoe of the quiet oil hydraulic actuator of pie graph 2, in example shown in Figure 7, piston shoe 98 has globular part 102 and roof pressure portion 104, is formed with vertically the oilhole 106 that (above-below direction of Fig. 7) connects in globular part 102 and the roof pressure portion 104.Roof pressure portion 104 side opening ends at oilhole 106 are provided with oil pressure hole 114, oil pressure hole 114 forms the tubular that the end is arranged of the internal face 116 with relative inclined, and to be internal diameter reduce towards roof pressure portion 104 outer surface directions (Fig. 7 below) interval between the internal face 116 gradually.That is to say that oil pressure hole 114 section configurations that are orthogonal to axial plane increase gradually towards the inboard.Therefore, even the sliding contact of the outer surface of the roof pressure portion 104 of piston shoe 98 and movable swash plate 74 (Fig. 2) is because long-term the use under the situation of wear and tear, on movable swash plate 74 with oil pressure hole 114 in bearing of facing of action oil phase move the area of oily pressure and increase gradually.Therefore, by the action oil in the oil pressure hole 114, can increase and act on the power that makes the direction that the movable relatively swash plate 74 of piston shoe 98 lifts, thereby can further reduce the wearing and tearing of piston shoe 98.
As shown in Figure 8, in variable bit be arranged on rotationally between lining 76 in the piston main body 96 and the cylinder chamber 94 and be provided with spring 72.Therefore, when cylinder body 68 relative drive shafts 16 rotate, even under the situation that piston main body 96 rotates in each cylinder chamber 94, also can prevent reversing of spring 72 effectively, and improve durability.Pump important document 38 comprises live axle 16, cylinder body 68, a plurality of piston 70, a plurality of spring 72, a plurality of lining 76 and movable swash plate 74.
When use comprised the oil pressure pump 12 of such pump important document 38, cylinder body 68 rotated with the rotation of live axle 16, and piston shoe 98 rotates along the plane of inclination 112 of movable swash plate 74, and slide in this plane of inclination 112 relatively.Therefore, each piston 70 to-and-fro motion, pressurized when vehicle advances from the action oil that the second oil circuit S2 (Fig. 3) is attracted in the pump important document 38, in the first oil circuit S1 (Fig. 3) that spues then.The action oil that spues among the first oil circuit S1 is fed into the hydraulic motor 14 that comprises motor important document 40 (Fig. 2).
This hydraulic motor 14 is described then.Hydraulic motor 14 possesses shell 34 and comprises the port seat 36 of motor valve plate 48.The both sides of motor valve plate 48 direction in the table of Fig. 2 have motor-side first port M1 (Fig. 1) and the motor-side second port M2 (Fig. 1) that slightly is circular arc respectively.The first port M1 leads to the first oil circuit S1 shown in Figure 3, and the second port M2 leads to the second oil circuit S2 (Fig. 3) shown in Figure 3.Therefore, the motor-side first port M1 is connected to the pump side first port P1 (Fig. 1) through the first oil circuit S1; The motor-side second port M2 is connected to the pump side second port P2 (Fig. 1) through the second oil circuit S2.
As shown in Figure 2, be provided with positive spline 128 in the axial intermediate portion of live axle 22 as spline part.Live axle 22 comprises the second positive spline 130, and this second positive spline 130 is arranged on the part promptly on the live axle outer circumferential face than the part of more close vertically port seat 36 sides of positive spline 128 of leaving positive spline 128 vertically, and its axial length is less than positive spline 128.The second positive spline 130 is arranged on the projection on the outer circumferential face of live axle 22.The back will describe the second positive spline 130 in detail.
The cylinder body 118, a plurality of piston 120, a plurality of spring 122 and a plurality of lining 126 that constitute hydraulic motor 14 have same structure with the cylinder body 68, a plurality of piston 70, a plurality of spring 72 and a plurality of lining 76 that constitute oil pressure pump 12 respectively.Fixedly swash plate 124 is bearing in the shell 34 obliquely with the predetermined angular of predefined relative drive shaft 22.Therefore, fixedly the angle of inclination of 124 pairs of live axles 22 of swash plate is constant.Piston shoe 98 (Fig. 9) roof pressure that constitutes each piston 120 is on the plane of inclination 132 of the fixedly swash plate 124 of the axioversion of relative drive shaft 22.Motor important document 40 comprises live axle 22, cylinder body 118, a plurality of piston 120, a plurality of spring 122, a plurality of lining 126 and fixing swash plate 124.
In the present embodiment, constitute port seat 36 shown in Figure 2 with a seat main body 44, pump valve plate 46 and motor valve plate 48, but also can omit valve plate 46,48, allow cylinder body 68,118 direct sliding contacts at port seat 36 promptly on the main body 44.In this case, the a pair of port that slightly is circular arc that will on the part in the face of the cylinder body 68 that constitutes oil pressure pump 12 of the internal surface of port seat 36, form, as pump side first port P1 and the pump side second port P2, and respectively a pair of port P1, P2 are led to the first oil circuit S1 and the second oil circuit S2.The a pair of port that slightly is circular arc that will on the part in the face of the cylinder body 118 that constitutes hydraulic motor 14 of the internal surface of port seat 36, form, as motor-side first port M1 and the motor-side second port M2, and respectively a pair of port M1, M2 are led to the first oil circuit S1 and the second oil circuit S2.
The hydraulic motor that comprises such motor important document 40 in use, the action oil of high pressure spues from pump important document 38 the first oil circuit S1, the oil that will move again is attracted to the pump important document 38 from the second oil circuit S2.Therefore, in motor important document 40, it is big that the high pressure action oil that attracts from the first oil circuit S1 by the motor-side first port M1 just makes the piston 120 corresponding to the cylinder chamber 94 (Fig. 9) that is communicated to the motor-side first port M1 leave the stretch amount of cylinder body 118.Therefore, piston 120 relative each cylinder chamber 94 to-and-fro motion, thereupon, cylinder body 118 and live axle 22 rotate.In this case, along with the rotation of cylinder body 118, the head of each piston 120 is that piston shoe 98 is along fixedly plane of inclination 132 rotations of swash plate 124, these plane of inclination 132 slips relatively.
Open put down in writing in the flat 5-50079 communique the same in fact with above-mentioned Japanese Patent Application Publication document, be arranged on each live axle 16,22 positive spline 88,128 with the chimeric situation of cloudy spline 92 keys of cylinder body 68,118 under, the axial middle position of key embedding part is arranged on the intersection point that the central shaft of common plane and live axle 16,22 of the center of rotation of the globular part 102 that comprises each piston shoe 98 intersects.Therefore, open put down in writing in the flat 5-50079 communique the same in fact with above-mentioned Japan, piston 70,120 switch to when spuing stroke from induction stroke, pressure in the cylinder chamber 94 sharply rises, the swash plate reaction force is added to the auxiliary section of piston main body 96 and piston shoe 98 from swash plate 74, in the swash plate reaction force, even with live axle 16, the component of the direction of 22 orthogonality of center shaft is added to the key embedding part, above-mentioned component also is to be added in equably on the whole length of spline embedding part, so can prevent from the spline embedding part, to produce mill partially, thereby improve cylinder body 68,118 durability.
In oil pressure pump 12 and hydraulic motor 14, between the inner peripheral surface of the outer circumferential face of live axle 16,22 and cylinder body 68,118, needn't be provided with and be used for the spring of piston 70,120 roof pressures to swash plate 74,124.Therefore, just radial dimension that will each cylinder body 68,118 is done greatly, can increase the quantity in cylinder chamber 94, perhaps the volume in each cylinder chamber 94 is done greatly, thereby has been realized the high capacity of oil pressure pump 12 and hydraulic motor 14.But, in this case, spring 72,122 must be set in each cylinder chamber 94.Therefore, if try every possible means on the structure of live axle 16,22 unlike present embodiment, the assembling work when assembling comprises the quiet oil hydraulic actuator 10 of oil pressure pump 12 and hydraulic motor 14 might be difficult to.That is to say, when this assembling work, the elastic force that imposes because of the spring 72,122 in the cylinder chamber 94 makes cylinder body 68,118 under the outstanding a lot of situation of the opening end of shell 34, the cloudy spline 92 of cylinder body 68,118 breaks away from positive spline 88,128, and the phase place of positive spline 88,128 and cloudy spline 92 might depart from.Under the situation of such phase deviation, very difficult one side is entrenched on the positive spline 88,128 cylinder body 68,118, and one side gives as security it into the inboard to shell 34.
For oil pressure pump 12, can under movable swash plate 74 is orthogonal to the state of central shaft of live axle 22, assemble, so cylinder body 68 can be smaller from shell 34 outstanding amounts with movable swash plate 74.With respect to this, for having the fixedly hydraulic motor 14 of swash plate 124, need carry out assembling work under with respect to the state of the inclined of live axle 22 at fixing swash plate 124, cylinder body 118 increases easily with respect to the overhang of shell 34.Therefore, if do not try every possible means on the structure of live axle 22, in the hydraulic motor 14, assembling work is difficulty especially.Present embodiment is exactly to improve such drawback.
That is to say that in the present embodiment, as mentioned above, the part of leaving the positive spline 88,128 on the outer circumferential face of each live axle 16,22 is provided with the second positive spline 90,130.The situation of oil pressure pump 12 at first, is described with Fig. 8.As shown in Figure 8, being arranged on the second positive spline 90 on the live axle 16 has the external diameter roughly the same with the external diameter that is formed on the spline tooth on the positive spline 88 (so-called " roughly the same external diameter " also comprises the situation of identical external diameter.Be intended to the containing of " roughly the same external diameter " in whole specification and claims all the same.)。Therefore, the spline tooth that forms on the second positive spline 90 has and the roughly the same external diameter of external diameter that is formed on the spline tooth on the positive spline 88.The second positive spline 90 comprise be formed on positive spline 88 on the second consistent spline tooth of spline tooth phase place.Another distolateral (right-hand member side of Fig. 8) at live axle 16 is provided with the flange 136 in order to prop up bearing 134, the external diameter of flange 136 is greater than the external diameter of the positive spline 88 and the second positive spline 90, is the external diameter of the 3rd positive spline 138 that links driving source and the be provided with external diameter less than the positive spline 88 and the second positive spline 90 in one distolateral (left end side of Fig. 8) of live axle 16.Therefore, when live axle 16 being inserted into cylinder body 68 inboard, just inserting and lead to piston opposition side (left side of Fig. 8) from the cylinder configuration side (right side of Fig. 8) of cylinder body 68.
Now just under state in the cylinder body 68 is separated and a plurality of pistons 70 and spring 72 all have been assembled to shell 34 and port seat 36 (Fig. 2 etc.), supported to situation in the shell 34 with being inserted into live axles 16 in the cylinder body 68, the situation of " in the assembly process " is analyzed.In this assembly process, as shown in Figure 8, each spring 72 is in cylinder body 68 under the situation of the length of freely growing, and the cloudy spline 92 of cylinder body 68 is positioned on the second positive spline 90.That is: the second positive spline 90 is chimeric with cloudy spline 92 keys of cylinder body 68.Under this state, limit the position of 90 pairs of live axles 16 of the second positive spline, to keep cylinder body 68 and the relative position of live axle 16 on sense of rotation.That is to say, no matter the elastic force that whether has spring 72 to give all is maintained cylinder body 68 and the relative position of live axle 16 on sense of rotation.
According to such formation, in above-mentioned assembly process, make the second positive spline 90 on the circumferencial direction of live axle 16, can contact cylinder body 68, the elastic force that can give at spring 72 will still be maintained cylinder body 68 and the relative position of live axle 16 on sense of rotation cylinder body 68 when the positive spline of live axle 16 is released.As shown in Figure 2, under the situation that shell 34 and port seat 36 have been combined, the second positive spline 90 breaks away from the cloudy spline 92 of cylinder body 68, thereby the second positive spline 90 can not be contacted with cylinder body 68.
The second positive spline 130 of the live axle 22 that constitutes motor important document 40 is described with Fig. 9.In this case, the situation with the live axle 16 of pump important document 38 is the same substantially.That is: the second positive spline 130 that is arranged on the live axle 22 has and the roughly the same external diameter of external diameter that is formed on the spline tooth on the positive spline 128.Therefore, the spline tooth that forms on the second positive spline 130 has and the roughly the same external diameter of external diameter that is formed on the spline tooth on the positive spline 128.The second positive spline 130 comprise be formed on positive spline 128 on the second consistent spline tooth of spline tooth phase place.Now just under state cylinder body 118 in is separated and a plurality of pistons 120 and spring 122 have been assembled to shell 34 and port seat 36 (Fig. 2 etc.), supported to shell 34 interior situations and thought that the situation of " in the assembly process " analyzes being inserted into live axles 22 in the cylinder body 118.In this assembly process, each spring 122 is in cylinder body 118 under the situation of the length of freely growing, and the cloudy spline 92 of cylinder body 118 is positioned on the second positive spline 130.Under this state, limit the position of the second positive spline 130, to keep cylinder body 118 and the relative position of live axle 22 on sense of rotation with respect to live axle 22.That is to say, no matter the elastic force that whether has spring 122 to give all is maintained cylinder body 118 and the relative position of live axle 22 on sense of rotation.
According to such formation, under the situation in above-mentioned assembly process, make the second positive spline 130 on the circumferencial direction of live axle 22, can contact cylinder body 118, the elastic force that can give at spring 122 will still be maintained cylinder body 118 and the relative position of live axle 22 on sense of rotation with cylinder body 118 when the positive spline 128 of live axle 22 is released.As shown in Figure 2, under the situation that shell 34 and port seat 36 have been combined, the second positive spline 130 breaks away from the cloudy spline 92 of cylinder body 118, thereby the second positive spline 130 can not be contacted with cylinder body 118.Can on each live axle 16,22, broach simultaneously and process the second positive spline 90,130 and positive spline 88,128.
According to such formation, the radial dimension that does not increase cylinder body 68 just can be realized high capacity, in this formation, under the situation in Fig. 8, assembly process shown in Figure 9, even the elastic force of the spring 72,122 in the cylinder chamber 94 makes cylinder body 68 under the outstanding situation of the opening end of shell 34, the phase place of sense of rotation that constitutes the cloudy spline 92 of the positive spline 88,128 of live axle 16,22 of spline embedding part and cylinder body 68,118 can not depart from yet.Therefore, can easily carry out the operation in conjunction with shell 34 and port seat 36, assembling work is also carried out easily.As a result, in the formation that cylinder chamber built-in spring is a spring 72,122 is set, realized the facilitation of assembling work.
The formation of other examples is described with Figure 10 to Figure 12 then.Figure 10 relates in the quiet oil hydraulic actuator of other examples of mode of execution of the present utility model to comprise corresponding to the expression of the downside of Fig. 2 the sectional view of the part of motor important document.Sectional view under the state in Figure 11 assembly process that to be the part that comprises the motor important document in the formation of expression Figure 10 separate on the member of band edge mouth and shell.Figure 12 is the sectional view of in the formation of Figure 11 a plurality of motor important documents being separated.
Figure 10 is to the situation of the formation of other examples shown in Figure 12, omitted at above-mentioned Fig. 1 to formation shown in Figure 9, the second positive spline 130 (with reference to Fig. 2, Fig. 9) on the outer circumferential face of the live axle 22 that constitutes hydraulic motor 14, replace, the part place of leaving positive spline 128 on this outer circumferential face vertically is provided with the ring-type teat 140 as projection.Ring-type teat 140 has the central shaft cylindraceous outer circumferential face 142 consistent with other parts of live axle 22, is provided with the step surface 144 that tilts with respect to axle direction between the small diameter portion of outer circumferential face 142 and both sides.The step surface 144 on one-sided (right side of Figure 10 to Figure 12) in the step surface 144 is the contacting part that can contact with cylinder body 118 vertically in assembly process described later.
Ring-type teat 140 has and the roughly the same external diameter of external diameter that is arranged on the spline tooth on the positive spline 128 on the live axle 22.As shown in figure 11, now just under state in the cylinder body 118 is separated and a plurality of pistons 120 and spring 122 have been assembled to shell 34 and port seat 36 (Figure 10), supported to situation on the shell 34 with being inserted into live axles 22 in the cylinder body 118, promptly the situation of " in the assembly process " is analyzed.In this case, as shown in figure 12, at first, live axle 22 is inserted in the cylinder body 118 to opposite side (from the right side of Figure 12 to the left side) from one-sided, in this state, the overhang bracket of live axle 22 to bearing 146, is blocked live axle 22 with back-up ring 148.In such assembly process, as shown in figure 11, ring-type teat 140 has limited moving axially of cylinder body 68; Limit the position of ring-type teat 140 relative drive shafts 22, chimeric with the key of the positive spline 128 of the cloudy spline 92 of keeping cylinder body 118 and live axle 22.That is to say that the one-sided step surface 144 of ring-type teat 140 contacts the end of cloudy spline 92 vertically, that is: the step surface 144 of ring-type teat 140 can contact cylinder body 118 vertically.Under this state, positive spline 128 is chimeric with cloudy spline 92 key on a part; Limit the position of ring-type teat 140 relative drive shafts 22, chimeric with the key that the positive spline 128 of keeping cylinder body 118 and live axle 22 forms.
According to such formation, under the situation in above-mentioned assembly process, the elastic force that can give at spring 122 will be maintained cylinder body 118 and the relative position of live axle 22 on sense of rotation with cylinder body 118 when the positive spline 128 of live axle 22 is released.As shown in figure 10, under the situation that shell 34 and port seat 36 have been combined, ring-type teat 140 breaks away from the cloudy spline 92 of cylinder body 118, thereby ring-type teat 140 can not be contacted with cylinder body 118.
Under the situation of this formation, also the Fig. 1 with above-mentioned is the same to the situation of formation shown in Figure 9, the radial dimension that does not increase cylinder body 118 just can be realized high capacity, in this formation, as shown in figure 11, in assembly process, even the elastic force of the spring 122 in the cylinder chamber 94 will be with cylinder body 68 under the outstanding situation of the opening end of shell 34, the phase place of sense of rotation that constitutes the cloudy spline 92 of the positive spline 128 of live axle 22 of spline embedding part and cylinder body 68 can not depart from yet.Therefore, can easily carry out operation, realize the facilitation of assembling work in conjunction with shell 34 and port seat 36.
Under the situation of this formation, in assembly process shown in Figure 11,, become the length of freely growing so can prevent spring 122 because cloudy spline 92 leans vertically on ring-type teat 140.Therefore, compare with the situation in the assembly process of above-mentioned formation shown in Figure 9, cylinder body 118 is little from the outstanding outstanding length L (Figure 11) of the opening end of shell 34.Therefore, use port seat 36 grades that cylinder body 118 is back into the operation of shell 34 inboards easily, assembling work is more prone to.All the situation with above-mentioned formation shown in Figure 9 is the same with effect for other formation.
In the above-mentioned oil pressure pump 12 of each above-mentioned configuration example, also can be the same with the hydraulic motor 14 of Figure 10 to Figure 12 explanation, on the outer circumferential face of the part of the positive spline 88 that axially leaves live axle 16, the second positive spline 90 is not set, but the ring-type teat that can contact with cylinder body 68 vertically in the assembly process is set.
Though omitted diagram, but also can go up and omit second positive spline 90,130 and the ring-type teat 140 at above-mentioned live axle 16 (or 22), replace, on above-mentioned live axle 16 (or 22), be provided as the large diameter ring-type teat of projection, this large diameter ring-type teat is arranged on the part of leaving positive spline 88,128 vertically, and its external diameter is greater than the external diameter of positive spline 88,128.And, in above-mentioned assembly process, also can allow large diameter ring-type teat, and axially at the piston side end face of cylinder body 68,118
The face of the inboard of the recess 150,152 (with reference to Fig. 8 to Figure 12) that falls into contacts vertically.Also can constitute above-mentioned ring-type teat or large-diameter annual teat with the member that the back-up ring on the outer circumferential face that is stuck in the axle itself that constitutes live axle 16,22 etc. is independent of axle itself.
In the superincumbent description, the situation that constitutes quiet oil hydraulic actuator 10 with oil pressure pump 12 and hydraulic motor 14 has been described.But, not the component part of oil pressure pump 12 or hydraulic motor 14, but under the situation about using as common independently oil pressure pump 12 or hydraulic motor 14, also can be suitable for the utility model as quiet oil hydraulic actuator.
Claims (5)
1. a ramp type hydraulic machinery possesses shell, be combined in the member of the band edge mouth on the described shell separably, be supported on the member of described shell and described band edge mouth and comprise the live axle that is arranged on the spline part on the outer circumferential face, be engaged on the described live axle and rotate integratedly with described live axle and slip cylinder body on the member of described band edge mouth by described spline part, but be configured in to to-and-fro motion a plurality of pistons in a plurality of cylinders chamber that is formed at described cylinder body, be arranged on a plurality of springs between described each cylinder chamber and described each piston, and be supported in the described shell and comprise the swash plate of the plane of inclination that described relatively in use live axle tilts;
The head of described piston is followed the rotation of described cylinder body and slide in the plane of inclination of described relatively swash plate, thereby makes described reciprocating motion of the pistons;
Described live axle comprises the projection on the outer circumferential face that is arranged on the part of leaving described spline part vertically;
Under state in the cylinder body is separated and a plurality of pistons and spring be assembled to the member of described shell and described band edge mouth, under the situation of drive shaft bearing in described shell that is inserted in the described cylinder body, just in assembly process, described projection can or axially contact described cylinder body along the circumferencial direction of described live axle; To by the elastic force of described spring when the spline part of described live axle is released, keep described cylinder body and the relative position of described live axle on sense of rotation at described cylinder body; Under the situation of the member combination of described shell and described band edge mouth, described projection does not contact with described cylinder body.
2. ramp type hydraulic machinery according to claim 1 is characterized in that described projection has and the roughly the same external diameter of external diameter that is formed on the key tooth on the described spline part.
3. ramp type hydraulic machinery according to claim 1 is characterized in that: described projection comprises second spline tooth, and the phase place of the key tooth on making it and being formed on described spline part is consistent; Limit the position of described projection with respect to described live axle, so that in described assembly process, described spring is in described cylinder body under the situation of free length, and described cylinder body is positioned on the described projection, and is maintained described cylinder body and the relative position of described live axle on sense of rotation.
4. ramp type hydraulic machinery according to claim 1 is characterized in that: described projection has the contacting part that can contact described cylinder body in described assembly process vertically; Limit the position of described projection with respect to described live axle, so that in described assembly process, the moving axially of the described cylinder body of described protrusions limit, thus it is chimeric to be maintained the key that described cylinder body and described live axle realized by described spline part.
5. quiet oil hydraulic actuator is characterized in that: possess oil pressure pump and be supplied to the pressure oil that spues from described oil pressure pump and the hydraulic motor that drives carried out quiet hydraulic transmission by described oil pressure pump and described hydraulic motor; One of described oil pressure pump and described hydraulic motor side or two sides are made of each described ramp type hydraulic machinery of claim 1 to 4; Constituting the shell of described oil pressure pump and the shell of the described hydraulic motor of formation is made of a common shell; Constituting the member of band edge mouth of described oil pressure pump and the member that constitutes the band edge mouth of described hydraulic motor is made of the member of a common band edge mouth.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010113079A JP5343037B2 (en) | 2010-05-17 | 2010-05-17 | Swash plate type hydraulic machine and hydrostatic transmission |
| JP2010-113079 | 2010-05-17 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202091108U true CN202091108U (en) | 2011-12-28 |
Family
ID=45366177
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011201558411U Expired - Lifetime CN202091108U (en) | 2010-05-17 | 2011-05-16 | Bevel board type hydraulic machinery and static oil pressure driving device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP5343037B2 (en) |
| CN (1) | CN202091108U (en) |
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| CN103998784A (en) * | 2012-03-26 | 2014-08-20 | 萱场工业株式会社 | Hydraulic pump motor |
| CN104100694A (en) * | 2013-04-10 | 2014-10-15 | 株式会社神崎高级工机制作所 | Movable Swash Plate Type Hydraulic Device |
| CN105202179B (en) * | 2015-08-26 | 2017-10-10 | 浙江奥威特液压机械有限公司 | A kind of hydrostatic stepless speed change device |
| CN111794937A (en) * | 2019-04-03 | 2020-10-20 | 纳博特斯克有限公司 | Pump unit and construction machine |
| CN111810351A (en) * | 2020-07-21 | 2020-10-23 | 黄鸿源 | Hydraulic generator |
| CN112984097A (en) * | 2019-12-02 | 2021-06-18 | Fte汽车有限责任公司 | Liquid pump |
| CN113374664A (en) * | 2021-07-13 | 2021-09-10 | 无锡威孚精密机械制造有限责任公司 | Plunger spring and cylinder body full circle contact structure of hydrostatic transmission device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013160319A (en) * | 2012-02-06 | 2013-08-19 | Sumitomo Heavy Ind Ltd | Hydraulic closed circuit system |
| JP6009770B2 (en) * | 2012-02-06 | 2016-10-19 | 住友重機械工業株式会社 | Hydraulic closed circuit system |
| JP2013164094A (en) * | 2012-02-09 | 2013-08-22 | Kanzaki Kokyukoki Manufacturing Co Ltd | Hydraulic continuously variable transmission |
| KR102654598B1 (en) * | 2022-10-31 | 2024-04-05 | 하이드로텍(주) | Hydrostatic Transmission |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5974346A (en) * | 1982-10-22 | 1984-04-26 | Toyota Motor Corp | Divided operation control type internal-combustion engine |
| JPH07189890A (en) * | 1993-12-27 | 1995-07-28 | Toyota Autom Loom Works Ltd | Axial piston pump |
-
2010
- 2010-05-17 JP JP2010113079A patent/JP5343037B2/en active Active
-
2011
- 2011-05-16 CN CN2011201558411U patent/CN202091108U/en not_active Expired - Lifetime
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103998784A (en) * | 2012-03-26 | 2014-08-20 | 萱场工业株式会社 | Hydraulic pump motor |
| CN103998784B (en) * | 2012-03-26 | 2015-08-05 | 萱场工业株式会社 | Fluid press pump motor |
| CN104100694A (en) * | 2013-04-10 | 2014-10-15 | 株式会社神崎高级工机制作所 | Movable Swash Plate Type Hydraulic Device |
| CN105202179B (en) * | 2015-08-26 | 2017-10-10 | 浙江奥威特液压机械有限公司 | A kind of hydrostatic stepless speed change device |
| CN111794937A (en) * | 2019-04-03 | 2020-10-20 | 纳博特斯克有限公司 | Pump unit and construction machine |
| CN111794937B (en) * | 2019-04-03 | 2024-05-28 | 纳博特斯克有限公司 | Pump unit and construction machine |
| CN112984097A (en) * | 2019-12-02 | 2021-06-18 | Fte汽车有限责任公司 | Liquid pump |
| CN111810351A (en) * | 2020-07-21 | 2020-10-23 | 黄鸿源 | Hydraulic generator |
| CN113374664A (en) * | 2021-07-13 | 2021-09-10 | 无锡威孚精密机械制造有限责任公司 | Plunger spring and cylinder body full circle contact structure of hydrostatic transmission device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2011241715A (en) | 2011-12-01 |
| JP5343037B2 (en) | 2013-11-13 |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term |
Granted publication date: 20111228 |
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| CX01 | Expiry of patent term |