CN101484727B - Hydraulic stepless transmission device - Google Patents

Abstract

A hydraulic stepless transmission having increased layout freedom and a compact structure with the functions of conventional hydraulic stepless transmission retained and having increased easiness of production. In the hydraulic stepless transmission (1), the movable swash plate (input side swash plate (6)) of a variable displacement plunger hydraulic pump or motor is tilted by a hydraulic servo mechanism (3). The hydraulic servo mechanism (3) has a power piston (15) connected to one end of the input side swash plate (6) and tilting it, a servo spool (13) placed normal to the direction of sliding of the power piston (15) and substantially in parallel to the input side swash plate (6), and a feedback link (24) for connecting the servo spool (13) and the input side swash plate (6).

Description

Hyaulic infinite variable speed mechanism

Technical field

The present invention relates to can be in various vehicles such as Motor Vehicle, agricultural operating vehicle the technology of widely used Hyaulic infinite variable speed mechanism.

Background technique

Past; Hyaulic infinite variable speed mechanism (HST) comprising: first and second rotatingshaft; Reciprocating first and second plunger on axial direction; Reciprocating first and second guiding valve on the same axis direction; Accommodate this first and second plunger, first and second guiding valve, with the cylinder body of the first rotatingshaft unitary rotation; On the swash plate face at the tilt angle of variable relative axis with the movable swash plate of the first plunger butt, axis relatively become on the swash plate face at the tilt angle of regulation with the second plunger butt and with the fixedly swash plate of the second rotatingshaft unitary rotation, the technology that in described Hyaulic infinite variable speed mechanism, constitutes the tilt angle of said movable swash plate has been disclosed and well-known variablely.

And in this Hyaulic infinite variable speed mechanism, the driving mechanism as the angle of inclination of the movable swash plate of oil hydraulic pump that is used to change adjustment variable volume type or oil pressure motor uses hydraulic servomechanism.

This hydraulic servomechanism because can obtain big driving force with little steering force, simultaneously, can precision easily be adjusted operation amount well, so be widely used as the driving adjustment means of the moving element of various devices.

But; The hydraulic servomechanism that is used for present hydraulic variable speed unit generally is to have in cylinder the piston that slips, produces as the big driving force of actual output; Built-in conduct is used for the hydraulic servomechanism of two-layer tube mode of servo guiding valve of the operation piece of positioning control in the inside of this piston; Because hydraulic servomechanism self becomes big in the ratio of producible driving force, so exist design to go up the low problem of degrees of freedom.

In addition; In technique known, the occasion of hydraulic servomechanism as the driving mechanism use of the movable swash plate in the Hyaulic infinite variable speed mechanism, formation makes hydraulic servomechanism and Hyaulic infinite variable speed mechanism separated structures; Near other hydraulic variable speed unit, set hydraulic servomechanism; Make structure, thus, be necessary to guarantee that installing space is abundant through the link mechanism transmission of drive force.

That is, according to such situation, it is difficult constituting Hyaulic infinite variable speed mechanism compactly.

In addition, in the prior art,, columned steel are implemented machining form a plurality of holes for the cylinder body that is applicable to Hyaulic infinite variable speed mechanism, and, to make through time taking operations such as borings, machining period is many.Thus, be difficult to make cylinder body.

In addition, owing to must carry out machining to the thin portion of cylinder body, it also is difficult making cylinder body self miniaturization, and thus, what make the Hyaulic infinite variable speed mechanism integral miniaturization also is difficult.

And then former said first and second each guiding valve reciprocatingly slides repeatedly through certain timing of being everlasting in device action and carries out the switching of oil circuit, because this is regularly once disorderly then Hyaulic infinite variable speed mechanism can not regular event, so must positively put timing in order.

In addition, the surface friction drag in the time of each guiding valve being slided prevents the technology of faults such as sintering when reducing, making each guiding valve successfully to slide as possible.

Summary of the invention

The problem that invention will solve

As the problem that will solve; The present invention provides a kind of and makes compact structure through the function of guaranteeing existing Hyaulic infinite variable speed mechanism and the degrees of freedom that can improve in the design; And when realizing improving making property; Really arrange timing that each guiding valve slides and the reliability that improves each guiding valve, realize improving the technology that the reliability of Hyaulic infinite variable speed mechanism improves.

Solve the means of problem

In Hyaulic infinite variable speed mechanism of the present invention; It is characterized in that; In the hydraulic pressure installation that the movable swash plate of oil hydraulic pump that makes the plunger type variable capacity type or hydraulic electric motor is fascinated by hydraulic servomechanism, said hydraulic servomechanism comprises: being connected with movable swash plate one end fascinates fascinating of driving is with piston, this glide direction with piston of fascinating feedback link of meeting at right angles direction and the servo guiding valve that disposes with said movable swash plate almost parallel, being connected this servo guiding valve and said movable swash plate relatively.

In addition, in Hyaulic infinite variable speed mechanism of the present invention, said hydraulic servomechanism is located at said servo guiding valve and said fascinating in the same shell with piston.

In addition; In Hyaulic infinite variable speed mechanism of the present invention, said hydraulic servomechanism disposes said feedback link with said fascinating with the piston almost parallel; Simultaneously; Make an end and the said movable swash plate pivotal connection of this feedback link, make middle part and said servo guiding valve pivotal connection, with the other end pivot suspension on said shell.

In addition; In Hyaulic infinite variable speed mechanism of the present invention; So that the center of rotation of the fulcrum of said feedback link and said movable swash plate is isolated to greatest extent; And the pivot connection of said feedback link and said movable swash plate and the center of rotation of said movable swash plate are isolated to greatest extent; And then the mode that the pivot connection of fulcrum and the said feedback link and the servo guiding valve of said feedback link is isolated to greatest extent disposes the pivot connection of said feedback link and said movable swash plate and the pivot connection of said feedback link and servo guiding valve.

In addition; In Hyaulic infinite variable speed mechanism of the present invention; Accommodate the center of rotation of the cylinder body of plunger to said fascinating with the piston break-through, compare with rectangular of the center of rotation of said movable swash plate and more be biased in of the side ground configuration of said plunger with the high pressure butt.

In addition, in Hyaulic infinite variable speed mechanism of the present invention, said fascinating is made up of the cylinder bar with piston.

In addition; In Hyaulic infinite variable speed mechanism of the present invention, make following structure; Promptly in the said occasion of fascinating and sliding to prolonging direction with piston, said hydraulic pressure installation rotates said movable swash plate with the mode to the action of speedup side, and; In the said occasion of fascinating and sliding to shrinkage direction with piston, said hydraulic pressure installation rotates said movable swash plate with the mode to the deceleration side action.

In addition; In Hyaulic infinite variable speed mechanism of the present invention, hydraulic pressure installation has disposed oil hydraulic pump and has used plunger on input shaft, and hydraulic electric motor is used plunger; Taken in the regularly cylinder body of guiding valve with axial direction with being free to slide abreast; With the movable swash plate of said oil hydraulic pump with the front end butt of plunger, with this movable swash plate opposition side and said hydraulic electric motor fixedly swash plate with the plunger butt, in this hydraulic pressure installation; On the same radius of said cylinder body mutual configuration a plurality of take in oil hydraulic pump with plunger and hydraulic electric motor with the hole of plunger, be provided with timing guiding valve reception hole with plunger hole and hydraulic electric motor with the central side between the plunger hole at this oil hydraulic pump.

In addition, in Hyaulic infinite variable speed mechanism of the present invention, in said cylinder body, oil hydraulic pump is used plunger hole with plunger hole and hydraulic electric motor, and the stream of the said timing guiding valve reception hole and the hydraulic oil of each plunger hole of coming in and going out is formed by core when casting.

In addition; In Hyaulic infinite variable speed mechanism of the present invention, hydraulic pressure installation has disposed oil hydraulic pump and has used plunger on input shaft, and hydraulic electric motor is used plunger; Parallel with axial direction, with being free to slide taken in the regularly cylinder body of guiding valve; With the movable swash plate of said oil hydraulic pump with the front end butt of plunger, this movable swash plate opposition side, with said hydraulic electric motor with the fixedly swash plate of plunger butt, in this hydraulic pressure installation; Be fixed in base side or the groove of an end of the said timing guiding valve of engaging fixedly is being set on the druum cam of swash plate side, this groove and the abutting part that is located at regularly the engagement portion of the front end of guiding valve are being constituted analyse and observe circular-arc.

In addition, in Hyaulic infinite variable speed mechanism of the present invention, the engagement portion of the front end that is located at said timing guiding valve constituted be roughly rectangular-shaped by analysing and observe of constituting of straight line.

In addition; In Hyaulic infinite variable speed mechanism of the present invention, on said fixedly swash plate, form the protuberance of two opposite side distance of separation shapes (two width of cloth shapes) at axle support inner face; And on said druum cam; Form the recess of two opposite side distance of separation shapes in axle support outside, formation makes said protuberance and the engaging of said recess, and said fixedly swash plate and said druum cam can not be fixedly installed with relatively rotating.

In addition; In Hyaulic infinite variable speed mechanism of the present invention; On said fixedly swash plate, form three protuberance different, and on said druum cam, form three recess different with the recess of said two opposite side distance of separation shapes in axle support outside with the protuberance of said two opposite side distance of separation shapes at axle support inner face; Make the engaging of said the 3rd protuberance and said the 3rd recess, can not fixedly install said fixedly swash plate and said druum cam with relatively rotating.

The effect of invention

In Hyaulic infinite variable speed mechanism of the present invention; Said hydraulic servomechanism comprises: being connected with movable swash plate one end fascinates fascinating of driving is with piston, this glide direction with piston of fascinating feedback link of meeting at right angles direction and the servo guiding valve that disposes with said movable swash plate almost parallel, being connected this servo guiding valve and said movable swash plate relatively, and hydraulic pressure installation can be realized miniaturization thus.In addition, can easily carry out the installation exercise of hydraulic pressure installation.And then, feedback mechanism is oversimplified.

In addition, in Hyaulic infinite variable speed mechanism of the present invention, be located at said servo guiding valve and said fascinating in the same shell with piston, thus, can make the hydraulic pressure installation miniaturization through said hydraulic servomechanism.

In addition, in Hyaulic infinite variable speed mechanism of the present invention, said hydraulic servomechanism and said fascinating are disposed said feedback link with the piston almost parallel; Simultaneously; Make an end and the said movable swash plate pivotal connection of this feedback link, make middle part and said servo guiding valve pivotal connection, with the other end pivot suspension on said shell; Thus, can constitute feedback link mechanism simple in structure, that precision is high.

In addition; In Hyaulic infinite variable speed mechanism of the present invention; So that the center of rotation of the fulcrum of said feedback link and said movable swash plate is isolated to greatest extent; And the pivot connection of said feedback link and said movable swash plate and the center of rotation of said movable swash plate are isolated to greatest extent; And then the mode that the pivot connection of fulcrum and the said feedback link and the servo guiding valve of said feedback link is isolated to greatest extent disposes the pivot connection of said feedback link and said movable swash plate and the pivot connection of said feedback link and servo guiding valve, can improve the resolving power of servomechanism thus.

In addition; In Hyaulic infinite variable speed mechanism of the present invention; Make said fascinating accommodate the center of rotation of the cylinder body of plunger with the piston break-through; Compare with rectangular of the center of rotation of said movable swash plate and more lean on the side ground bias configuration of said plunger, can prevent that thus unsuitable stress is added on the movable swash plate with the high pressure butt.In addition, movable swash plate is successfully rotated.

In addition, in Hyaulic infinite variable speed mechanism of the present invention, use piston, can make the hydraulic pressure installation miniaturization through constitute said fascinating by the cylinder bar.

In addition; In Hyaulic infinite variable speed mechanism of the present invention, through making following structure, promptly in the said occasion of fascinating and sliding to prolonging direction with piston; Said hydraulic pressure installation rotates said movable swash plate with the mode to the action of speedup side; And in the said occasion of fascinating and sliding to shrinkage direction with piston, said hydraulic pressure installation rotates said movable swash plate with the mode to the deceleration side action, can make the piston footpath and supply with hydraulic pressure to diminish.

In addition; In Hyaulic infinite variable speed mechanism of the present invention; Through a plurality of oil hydraulic pumps of taking in of mutual configuration on the same radius of said cylinder body with plunger and hydraulic electric motor hole with plunger; Be provided with regularly guiding valve reception hole with plunger hole and hydraulic electric motor with the central side between the plunger hole at this oil hydraulic pump, the wall thickness between the hole that can guarantee to accommodate the hole of plunger and accommodate guiding valve also can make the cylinder body miniaturization.

In addition, when the boundary dimension of cylinder body is constant, accommodates the hole of plunger and can do to carry out the processing in hole easily greatly with the bore of accommodating the hole of guiding valve.

In addition; In Hyaulic infinite variable speed mechanism of the present invention, because oil hydraulic pump is used plunger hole with plunger hole and hydraulic electric motor, the stream of the said timing guiding valve reception hole and the hydraulic oil of each plunger hole of coming in and going out is formed by core when casting; Can reduce manufacturing procedures such as cutting hole; In addition, owing to can omit the necessary stopper etc. of inaccessible cutting hole end, can reduce component number.Thus, can make cylinder body at an easy rate.

In addition, stop up the necessary muscle of processing cutting bore ends owing to can omit, so can make the cylinder body miniaturization and.

In addition; In Hyaulic infinite variable speed mechanism of the present invention; Hydraulic pressure installation has disposed oil hydraulic pump and used plunger on input shaft, hydraulic electric motor is used plunger, and is parallel with axial direction, with being free to slide taken in the regularly cylinder body of guiding valve; With the movable swash plate of said oil hydraulic pump with the front end butt of plunger; This movable swash plate opposition side, with said hydraulic electric motor with the fixedly swash plate of plunger butt, in this hydraulic pressure installation, be fixed in base side or the groove of an end that engages said timing guiding valve fixedly be set on the druum cam of swash plate side; It is circular-arc that abutting part formation with the engagement portion front end that is located at the timing guiding valve this groove is analysed and observe, and can prevent the regularly sintering of guiding valve thus.In addition, can making regularly, guiding valve successfully slides.

In addition, in Hyaulic infinite variable speed mechanism of the present invention, constitute by what straight line constituted through the engagement portion that makes the front end of being located at said timing guiding valve and to analyse and observe essentially rectangular, can making regularly, the processing of guiding valve becomes easy.In addition, can making regularly, guiding valve successfully slides.

In addition; In Hyaulic infinite variable speed mechanism of the present invention,, form the protuberance of two opposite side distance of separation shapes at axle support inner face through making on said fixedly swash plate; And on said druum cam; Form the recess of two opposite side distance of separation shapes in axle support outside, make the engaging of said protuberance and said recess, the structure that said fixedly swash plate and said druum cam can not be fixedly installed with relatively rotating; Can make regularly the phase place of guiding valve consistent really, can obtain the timing that oil circuit switches really.In addition, can easily carry out installation exercise.

In addition; In Hyaulic infinite variable speed mechanism of the present invention; Through making on said fixedly swash plate, form three protuberance different at axle support inner face with the protuberance of said two opposite side distance of separation shapes, and on said druum cam; Form three recess different in axle support outside with the recess of said two opposite side distance of separation shapes; Make the engaging of said the 3rd protuberance and said the 3rd recess, the structure that said fixedly swash plate and said druum cam can not be fixedly installed with relatively rotating can prevent the installation error when hydraulic pressure installation is installed.In addition, can carry out installation exercise easily.

Description of drawings

Fig. 1 is the side partial sectional view of structure of integral body of the Hyaulic infinite variable speed mechanism of expression one embodiment of the invention.

Fig. 2 is the integrally-built stereogram of expression Hyaulic infinite variable speed mechanism.

Fig. 3 is the integrally-built stereogram of expression input side housing.

Fig. 4 is the side partial sectional view of formation of the hydraulic servomechanism of expression one embodiment of the invention.

Fig. 5 is the stereogram of the cylinder body of expression one embodiment of the invention.

Fig. 6 is the rear view of this cylinder body of expression.

Fig. 7 is A-A sectional view and the B-B sectional view of this Fig. 5.

Fig. 8 is the stereogram of this B-B section of expression.

Fig. 9 is the plan view of the timing guiding valve of expression one embodiment of the invention.

Figure 10 is the stereogram of this timing guiding valve of expression.

The side partial sectional view of the timing guiding valve when Figure 11 is this cylinder body insertion of expression.

Figure 12 is the ideograph of a series of actions of timing guiding valve and the plunger of expression one embodiment of the invention.

Figure 13 is the stereogram of the guiding valve cam of expression one embodiment of the invention.

Figure 14 is the plan view of this guiding valve cam of expression.

Figure 15 is the left side view of this guiding valve cam of expression.

Figure 16 is the plan view of this guiding valve cam of expression.

Figure 17 is the enlarged view of this input side guiding valve cam engagement portion.

Figure 18 is the stereogram of the outlet side swash plate of expression one embodiment of the invention.

Figure 19 is the plan view of this outlet side swash plate of expression.

Figure 20 is the left side view of this outlet side swash plate of expression.

Figure 21 is the system diagram of hydraulic path of the non-return safety valve of expression one embodiment of the invention.

Figure 22 is the unfolded drawing of first mode of the hydraulic servomechanism of expression one embodiment of the invention.

Figure 23 is the unfolded drawing of second mode of this hydraulic servomechanism of expression.

Figure 24 is the unfolded drawing of the Third Way of this hydraulic servomechanism of expression.

Figure 25 is the hydraulic scheme of this hydraulic servomechanism.

Symbol description

1 Hyaulic infinite variable speed mechanism

3 hydraulic servomechanisms

6 input side swash plates

13 servo guiding valves

15 power pistons

24 feedback links

Embodiment

The working of an invention mode is described below.

Fig. 1 is the integrally-built side partial sectional view of the Hyaulic infinite variable speed mechanism of expression one embodiment of the invention, and Fig. 2 is the integrally-built stereogram of expression Hyaulic infinite variable speed mechanism, and Fig. 3 is the integrally-built stereogram of expression input side housing; Fig. 4 is the side partial sectional view of formation of the hydraulic servomechanism of expression one embodiment of the invention; Fig. 5 is the stereogram of the cylinder body of expression one embodiment of the invention, and Fig. 6 is the rear view of this cylinder body of expression, and Fig. 7 is A-A sectional view and the B-B sectional view of this Fig. 5; Fig. 8 is the stereogram of this B-B section of expression; Fig. 9 is the plan view of the timing guiding valve of expression one embodiment of the invention, and Figure 10 is the stereogram of this timing guiding valve of expression, the side partial sectional view of the timing guiding valve when Figure 11 is this cylinder body insertion of expression; Figure 12 is the ideograph of a series of actions of timing guiding valve and the plunger of expression one embodiment of the invention; Figure 13 is the stereogram of the guiding valve cam of expression one embodiment of the invention, and Figure 14 is the plan view of this guiding valve cam of expression, and Figure 15 is the left side view of this guiding valve cam of expression; Figure 16 is the plan view of this guiding valve cam of expression; Figure 17 is the enlarged view of this input side guiding valve cam engagement portion, and Figure 18 is the stereogram of the outlet side swash plate of expression one embodiment of the invention, and Figure 19 is the plan view of this outlet side swash plate of expression; Figure 20 is the left side view of this outlet side swash plate of expression; Figure 21 is the system diagram of hydraulic path of the non-return safety valve of expression one embodiment of the invention, and Figure 22 is the unfolded drawing of first mode of the hydraulic servomechanism of expression one embodiment of the invention, and Figure 23 is the unfolded drawing of second mode of this hydraulic servomechanism of expression; Figure 24 is the unfolded drawing of the Third Way of this hydraulic servomechanism of expression, and Figure 25 is the hydraulic scheme of this hydraulic servomechanism.

At first, with Fig. 1 to Figure 21 the overall structure of the Hyaulic infinite variable speed mechanism 1 of one embodiment of the invention is described.

In addition, for the ease of the explanation, the direction of the arrow A shown in Fig. 1 as the place ahead.

As shown in Figure 1; The Hyaulic infinite variable speed mechanism 1 of one embodiment of the invention is made up of the oil hydraulic pump of variable capacity type and the hydraulic electric motor of fixed capacity type; Mainly by constituting with lower component; That is: input shaft 2; Reciprocating input side plunger 8,8... on the axial direction of said input shaft 2 as first plunger; As outlet side plunger 10, the 10... of second plunger, reciprocating input side timing guiding valve 9,9... as first guiding valve on the same axis direction are as outlet side timing guiding valve 11, the 11... of second guiding valve; Accommodate the cylinder body 7 of said each plunger 8,10 and each timing guiding valve 9,11 and input shaft 2 unitary rotation; On the swash plate face at the tilt angle of variable relative axis, with the input side swash plate 6 of said input side plunger 8,8... butt, become on the swash plate face at the tilt angle of regulation at axis relatively, with said outlet side plunger 10,10... butt in the outlet side swash plate 12 that rotates, as the hydraulic servomechanism 3 of the driving mechanism of said input side swash plate 6 etc.

In the Hyaulic infinite variable speed mechanism 1 of present embodiment, regularly guiding valve 9, input side guiding valve cam 37 etc. constitute oil hydraulic pump by swash plate holding member 5, input side swash plate 6, cylinder body 7, input side plunger 8, input side; In addition, regularly guiding valve 11, outlet side guiding valve cam 47, outlet side swash plate 12 etc. constitute hydraulic electric motor by cylinder body 7, outlet side plunger 10, outlet side.

Like this, make the structure of each plunger 8,10 of in a cylinder body 7, taking in oil hydraulic pump and hydraulic electric motor, can realize compactness.

Below carry out the detailed description of input shaft 2 with Fig. 1.

Input shaft 2 is the axles that are used for pass to Hyaulic infinite variable speed mechanism 1 from drive source drives power such as motors; Be used for being located in axial direction to the oil circuit 2b of Hyaulic infinite variable speed mechanism 1 each supply hydraulic oil at axis central part, the substantial middle portion at axial direction has the wide diameter portion that is used to be provided with non-return safety valve 38a, 38b in addition.Input shaft 2 rotates through input side tapered roller bearing 21 and input side needle roller bearing 22 and freely is bearing on the input side housing 4 by axle.The inner ring of this input side tapered roller bearing 21 can not be fixed by pad 60 with from the input side bearing tightening nut 23 relative input shafts 2 that the front end 2a side of input shaft 2 screws togather installation rotationally.In addition, cylinder body 7 can not be fixed on the input shaft 2 through spline is chimeric with relatively rotating.

Below carry out a detailed description with Fig. 1 to Fig. 4 as the input side housing 4 of the bearing part of the said input shaft 2 of axle supporting.

To shown in Figure 3, input side housing 4 is made up of each one of adjustment part 3b as the carry-out part 3a of the cartridge housing body 4a of the basic comprising part of this input side housing 4, the hydraulic servomechanism 3 that above this cartridge housing body 4a, forms and the hydraulic servomechanism 3 that forms towards the direction of advance of said cartridge housing body 4a and at left like Fig. 1.

In addition, do not limit the collocation method of the carry-out part 3a, adjustment part 3b etc. of these hydraulic servomechanisms 3, can suitably change.

In cartridge housing body 4a, be equipped with the through hole that is used to connect said input shaft 2, the foreign steamer of input side tapered roller bearing 21 is entrenched in the inner peripheral surface front portion of this through hole, and input side needle roller bearing 22 is entrenched in the inner peripheral surface rear portion.

Like Fig. 1 to shown in Figure 3, the carry-out part 3a of hydraulic servomechanism 3 by the carry-out part cylinder 4b that forms along fore-and-aft direction above the said cartridge housing body 4a, in this carry-out part cylinder 4b can along fore-and-aft direction slidingly back and forth slotting power piston 15 and the fixed component 16 etc. that is fixedly installed on the rearward end of this power piston 15 constitute.

Form wide diameter portion 15a at the front end of power piston 15, constitute grease chamber, front side 17 by front-end face and the carry-out part cylinder 4b of this wide diameter portion 15a, the while, ear end face and the carry-out part cylinder 4b by this wide diameter portion 15a constituted rear side grease chamber 18.In addition, through hydraulic pressure in each grease chamber 17,18 being changed to make power piston 15 to reciprocatingly slide along fore-and-aft direction.

In the wall portion of the front side of grease chamber, said front side 17, screw togather adjustment bolt 19 is set, constitute the rearward end of this adjustment bolt 19 and the front-end face butt of said wide diameter portion 15a.

Through such formation, adjustment makes adjustment bolt 19 face the inner length of carry-out part cylinder 4b, can limit the sliding position to the front side of power piston 15.In addition, make the structure that to use locking nut 53 to fix to adjustment bolt 19, can keep making adjustment bolt 19 to face the inner length of carry-out part cylinder 4b.

Fixed component 16 be the input side swash plate 6 stated after fixing fixing part 6c analyse and observe the parts that are roughly the コ font so that the open sides of コ word mode downwards is fixedly installed on the rearward end of said power piston 15.

Like this, power piston 15 is made up of the cylinder bar, thus, can make Hyaulic infinite variable speed mechanism 1 miniaturization.

In addition, in the present embodiment, power piston 15 is made up of the cylinder bar, make the structure that helps the whole miniaturization of hydraulic pressure installation, but the structure of power piston 15 is not limited thereto.

As shown in Figure 4, the adjustment part 3b of hydraulic servomechanism 3 by the left sidepiece of said cartridge housing body 4a adjustment part cylinder 4c that above-below direction forms, in be inserted among the cylinder 4c of this adjustment part to be inserted into the feedback pilot valve 14 among the cylinder 4c of adjustment part in can be at servo guiding valve 13 that above-below direction constitutes slidingly back and forth, below this servo guiding valve 13 and to be installed in spring members 20 in servo guiding valve 13 and the feedback pilot valve 14 etc. and constitute.

Servo guiding valve 13 is made the structure with a plurality of wide diameter portions (lip part) and diameter reducing part, has successively from upside: the first wide diameter portion 13a, the first diameter reducing part 13b, the second wide diameter portion 13c, the second diameter reducing part 13d, the 3rd wide diameter portion 13e, the 3rd diameter reducing part 13f, the 4th wide diameter portion 13g, the 4th diameter reducing part 13h and the 5th wide diameter portion 13i.

In addition, wear oil circuit 13m on the core at the axle of servo guiding valve 13 from the lower end surface 13j of servo guiding valve 13 to the above-below direction substantial middle portion of the first wide diameter portion 13a.This oil circuit 13m makes following structure, is not doing on the illustrated hydraulic pressure oil tank 27 through being located in the inner oil circuit connection of cartridge housing body 4a, and hydraulic oil is directed to hydraulic pressure oil tank 27 through this oil circuit 13m and connection mouth 4q.And then this oil circuit 13m makes oil circuit 13n that connection wears at the first diameter reducing part 13b and the structure of the oil circuit 13p that wears at the 3rd diameter reducing part 13f.

Adjustment part cylinder 4c is by the first bulge 4d that has with the roughly the same internal diameter size of the outside dimension of each wide diameter portion 13a of servo guiding valve 13,13c, 13e, 13g, 13i; Have the second bulge 4e with the roughly the same internal diameter size of the boundary dimension of the wide diameter portion of feedback pilot valve 14, have the internal diameter size that to accommodate spring members 20, the contraction flow region 4f that is communicated with the first bulge 4d and the second bulge 4e constitutes.

The top of the first bulge 4d is by stopper 54 obturations, forms grease chamber, top 39 by the upper-end surface 13k of this stopper 54 and the first bulge 4d and servo guiding valve 13.In addition, this grease chamber, top 39 is communicated with by oil circuit 4g with ratio adjustment valve 25, makes and can adjust valve 25 by resize ratio, can adjust the structure of the hydraulic pressure in the grease chamber, top 39.

The outside dimension that middle part forms each wide diameter portion 13a than servo guiding valve 13,13c, 13e, 13g, 13i above the first bulge 4d is the grease chamber, top 40 of expansion further, makes the structure of this grease chamber, top 40 and 18 usefulness the oil circuit 4h of said rear side grease chamber connection.This grease chamber, top 40 is according to the upper-lower position of servo guiding valve 13; Obtain being communicated with the first diameter reducing part 13b of servo guiding valve 13 or being communicated with, or keep and other three kinds of so-called different modes of disconnected states such as grease chamber with the second diameter reducing part 13d of servo guiding valve 13.

In addition; Middle part also forms and compares the further grease chamber, bottom 44 that has expanded with the outside dimension of each wide diameter portion 13a of guiding valve 13,13c, 13e, 13g, 13i below the first bulge 4d, makes the structure that this grease chamber, bottom 44 and grease chamber, said front side 17 are communicated with by oil circuit 4i.This grease chamber, bottom 44 is same with grease chamber 40, said top; Upper-lower position according to servo guiding valve 13; Obtain being communicated with the second diameter reducing part 13d of servo guiding valve 13; Or be communicated with, or keep and other three kinds of so-called different modes of disconnected states such as grease chamber with the 3rd diameter reducing part 13f of servo guiding valve 13.

In addition; The space that forms by the second diameter reducing part 13d and the adjustment part cylinder 4c of servo guiding valve 13 by oil circuit 4j with do not make illustrated supply pump 26 and be communicated with; Supply with the hydraulic oil of high pressure to the grease chamber that is communicated with this second diameter reducing part 13d (that is any in grease chamber, top 40 or the grease chamber, bottom 44).

Promptly; Hydraulic servomechanism 3 is made power piston 15, servo guiding valve 13 is located at the structure on the input side housing 4 of same shell, thus, can make Hyaulic infinite variable speed mechanism 1 miniaturization; In addition, can make both as much as possible near disposing, oil channel structures being shortened.

As shown in Figure 4, feedback pilot valve 14 is made up of first and second enlarged portion 14a, 14c and the portion 14b of dwindling that have with the roughly consistent boundary dimension of the internal diameter size of the second bulge 4e.

Dwindle at this that the formation activity is combined with link pin 34 in recess that 14b of portion forms, according to the upper and lower displacement of this link pin 34, also upper and lower displacement of feedback pilot valve 14.

In addition, link pin 34 is faced the arranged outside of adjustment part cylinder 4c from the window portion of the slotted hole shape of the left surface formation of the cylinder 4c in the adjustment part.In addition, on feedback link 24, the angle that constitutes this link pin 34 and input side swash plate 6 is relevant, the structure of upper and lower displacement link pin 34 pivot suspensions.

Like this, the hydraulic servomechanism 3 of present embodiment is made carry-out part 3a and adjustment part 3b separated structures, through link carry-out part 3a and adjustment part 3b with feedback link 24 design freedom of hydraulic servomechanism 3 is improved.

Promptly; In the Hyaulic infinite variable speed mechanism 1 that the oil hydraulic pump of plunger type variable capacity type or the movable swash plate of hydraulic electric motor (input side swash plate 6) are fascinated; Said hydraulic servomechanism 3 is made the structure that has with lower component, promptly has: be connected an end of input side swash plate 6, the power piston 15 that fascinates and drive; The relative glide direction of power piston 15 direction that meets at right angles, and with the servo guiding valve 13 of the plate face almost parallel configuration of input side swash plate 6; With the feedback link 24 that is connected servo guiding valve 13 and input side swash plate 6; Thus; Can make servo guiding valve 13 and the 6 as close as possible configurations of input side swash plate, owing at an upper portion thereof power piston 15 is configured on the right angle orientation, so can make Hyaulic infinite variable speed mechanism 1 miniaturization.In addition, because at the top of cartridge housing body 4a configuration hydraulic servomechanism 3, at sidepiece configuration feedback link 24, so can easily carry out the installation exercise of Hyaulic infinite variable speed mechanism 1.In addition, feedback mechanism is oversimplified.

Below carry out the detailed description of swash plate holding member 5 with Fig. 1 or Fig. 2.

Like Fig. 1 or shown in Figure 2; Swash plate holding member 5 is in abutting connection with the rear that is provided in said cartridge housing body 4a; Be the tilt angle (the axis angulation of swash plate face 6a and input shaft 2) that can change the swash plate face 6a of input side swash plate 6, the parts that are used to support input side swash plate 6, wear porose in substantial middle.In addition, swash plate holding member 5 relative cartridge housing body 4a fix with bolton.

The rearward end of swash plate holding member 5 (holding part 5a) has the roughly hollow shape of semicircle shape.Fixedly install swash plate with metal bearing 28 at the hollow position of this semicircle shape with spring pin etc.

Below use Fig. 1, Fig. 2 or Figure 22 carry out the detailed description of input side swash plate 6.

Like Fig. 1; Fig. 2 or shown in Figure 22; Input side swash plate 6 is to convert the rotating drive power of input shaft 2 to input side plunger 8 reciprocating power (that is, the hydraulic pressure of the hydraulic oil in the oil hydraulic circuit that in cylinder body 7, forms), simultaneously; The parts of the stroke when changing 8 to-and-fro motion of input side plunger (, the amount of the hydraulic oil of force feed during 8 to-and-fro motion of input side plunger) through the tilt angle that changes swash plate face 6a.Input side swash plate 6 is the parts that wear the hole of input shaft 2 perforations in substantial middle, forms the swash plate face 6a that it simultaneously is a platen surface.

The protruding terminus of input side plunger 8 (butt dish 8c) butt (or engaging) is on swash plate face 6a.In addition, the outstanding holding part 6b that is provided with on another plate face.The shape of holding part 6b is corresponding with the hollow position of the semicircle shape of the holding part 5a of said swash plate holding member 5; Input side swash plate 6 can change the tilt angle (the axis angulation of swash plate face 6a and input shaft 2) of swash plate face 6a with holding part 5a (saying it is to be located at the swash plate of hollow of semicircle shape in the side-looking with the metal bearing 28) butt and the rotation of holding part 6b and swash plate holding member 5 tightlyer.

In addition, even the diameter in the hole that the substantial middle of input side swash plate 6 wears rotates the also hands-off size of input shaft 2 for input side swash plate 6.

Below use Fig. 1, Fig. 2 and Fig. 5 to Fig. 8 are elaborated to the cylinder body 7 mode of execution, critical piece of the present invention as the cylinder body of hydraulic pressure installation of the present invention.

Like Fig. 1; Fig. 2 and shown in Figure 5; Cylinder body 7 is parts of substantial cylindrical shape; Wear the through hole 7c that connect input shaft 2 from input side end face 7a to outlet side end face 7b in the substantial middle portion of cylinder body 7, implement spline processing at the front end (end of input side end face 7a side) of the inner peripheral surface of this through hole 7c.In addition, when input shaft 2 is installed, on the outer circumferential face of the input shaft 2 corresponding with the position of the processing spline of said cylinder body 7, also implement spline processing on cylinder body 7, cylinder body 7 can not relatively rotate ground rotation integratedly with input shaft 2 splines are chimeric.

Input side end face 7a is and input side swash plate 6 face in opposite directions that outlet side end face 7b is and outlet side swash plate 12 face in opposite directions.Input side end face 7a and outlet side end face 7b any all with the orthogonal axe of input shaft 2.

, in cylinder body 7, wear to the axial direction of input shaft 2 from the input side end face 7a of cylinder body 7 and to amount to seven input side plunger holes 31,31... and to amount to seven places' input sides regularly sliding valve hole 32,32... to shown in Figure 8 like Fig. 6.

Input side plunger hole 31,31... are the holes that on cylinder body 7, wears that is used to accommodate input side plunger 8,8..., the parallel axes of its long side direction and input shaft 2.In addition, input side plunger hole 31,31... do not penetrate into outlet side end face 7b, through the position of depending on outlet side end face 7b than the position intermediate of input side end face 7a and outlet side end face 7b slightly.

Input side regularly sliding valve hole 32,32... is used to accommodate the regularly hole that on cylinder body 7, wears of guiding valve 9,9... of input side, the parallel axes of its long side direction and input shaft 2.In addition, regularly sliding valve hole 32,32... penetrate into outlet side end face 7b to input side.

As shown in Figure 6; Input side plunger hole 31,31... see from the axial direction of input shaft 2; Input shaft 2 is from connecting the through hole 7c equidistant (on the concentric circle) that installs, and the distance of 31,31 of the input side plunger holes of adjacency becomes equidistant and disposes (through hole 7c axle center becomes equal angles relatively).

In addition; Input side regularly sliding valve hole 32,32... is seen from the axial direction of input shaft 2; Input shaft 2 is also from the through hole 7c equidistant (on the concentric circle) that connect to install, and the input side of adjacency regularly the distance of 32,32 of sliding valve holes become equidistant and dispose (through hole 7c axle center becomes equal angles relatively).And then input side regularly sliding valve hole 32,32... is nearer from the distance of through hole 7c than input side plunger hole 31,31..., and the distance of the outlet side plunger hole of stating after input side plunger hole 31 and the adjacency 41 becomes equidistantly to dispose.That is, through the center of through hole 7c, and, make on the symmetrical line segment of line between the input side outlet side plunger hole 41 that regularly center configuration of sliding valve hole 32 is stated after adjacent with it input side plunger hole 31.

Like Fig. 6 to shown in Figure 8, the input side plunger hole 31 that on cylinder body 7, wears and the input side of this nearest adjacency regularly sliding valve hole 32 be provided with 7 groups as one group, input side plunger hole 31 of each group is communicated with respectively with input side timing sliding valve hole 32 usefulness intercommunicating pores 33.

At this moment, intercommunicating pore 33,33... on the axial direction of input shaft 2, be located in the position of the substantial middle of cylinder body 7, input side plunger hole 31 and input side regularly are communicated with the shortest between the axle center of sliding valve hole 32, more tilt than radial direction.

In the present embodiment,, make mo(u)lding to cylinder body 7, when casting, adopt the method for using the shell core to form as the formation method of this intercommunicating pore 33,33....Thus, can reduce the man-hour of machining, simultaneously, can not stop up the necessary obstruction in cutting hole end and handle and stop up and handle necessary muscle etc., can reduce the lightweight of component number, realization cylinder body.

Promptly; In cylinder body 7, at input side plunger hole 31,31... and outlet side plunger hole 41,41..., each is sliding valve hole 32,32... and 42,42... regularly; The stream of the hydraulic oil that each plunger hole 31,31... and 41,41... come in and go out is formed by the casting method of having used the shell core.

Thus, can reduce manufacturing procedures such as cutting hole, in addition, owing to can omit the inaccessible needed stopper etc. of cutting hole end, so can reduce number of components.Therefore, can make cylinder body 7 at an easy rate.

In addition, handle needed muscle owing to can omit the obstruction of said cutting hole end, so can make cylinder body 7 miniaturization ands.

In addition, as the diameter input side of the interflow portion 36 of the interflow portion of intercommunicating pore 33,33... and input side plunger hole 31,31... regularly the internal diameter hole enlargement of sliding valve hole 32 form.Through such formation; When regularly the wide diameter portion 9a of guiding valve 9 interdicts input side plunger hole 31 with input side grease chamber 35 and outlet side grease chamber 45 by input side (neutral position); Can prevent that owing to the periphery to wide diameter portion 9a acts on hydraulic pressure equably input side regularly guiding valve 9 is pressed to the specific circumferencial direction as the inside of input side timing sliding valve hole 32.

To shown in Figure 8, in cylinder body 7, be equipped with totally seven outlet side plunger holes 41,41... and regularly sliding valve hole 42,42... of totally seven places' outlet sides to the axial direction of input shaft 2 like Fig. 6 from the outlet side end face 7b of cylinder body 7.

Outlet side plunger hole 41,41... are used to the hole of accommodating outlet side plunger 10,10, on cylinder body 7, wearing, the parallel axes of its long side direction and input shaft 2.In addition, outlet side plunger hole 41,41... do not penetrate into input side end face 7a, through the position of depending on input side end face 7a than the position intermediate that becomes input side end face 7a and outlet side end face 7b slightly.

Outlet side regularly sliding valve hole 42,42... is used to accommodate outlet side regularly guiding valve 11,11..., the hole that on cylinder body 7, wears, the parallel axes of its long side direction and input shaft 2.In addition, regularly sliding valve hole 42,42... penetrate into input side end face 7a to outlet side.

As shown in Figure 6; See from the axial direction of input shaft 2; Outlet side plunger hole 41,41... are configured to from the through hole 7c equidistant (on the concentric circle) that input shaft 2 connect to be installed, and the distance of 41,41 of the outlet side plunger holes of adjacency becomes equidistant (the relative axle center of through hole 7c equal angles).

In addition; See from the axial direction of input shaft 2; Outlet side regularly sliding valve hole 42,42... also is configured to the through hole 7c equidistant (on the concentric circle) that input shaft 2 is installed from connecting, and the outlet side of adjacency regularly the distance of 42,42 of sliding valve holes be equidistant (the relative axle center of through hole 7c equal angles).And then outlet side regularly sliding valve hole 42,42... specific output lateral column consent 41,41... is near from the distance of through hole 7c, and also becomes configuration equidistantly from any of the said input side plunger hole 31 of outlet side plunger hole 41 and adjacency.That is, the center through through hole 7c and make outlet side plunger hole 41 and input side plunger hole 31 between become on the line segment of line symmetry the regularly center of sliding valve hole 42 of configuration outlet side.

Like Fig. 6 to shown in Figure 8, in outlet side plunger hole 41 with the outlet side that sets recently regularly sliding valve hole 42 be one group and be provided with seven groups altogether, regularly wear intercommunicating pore 43 respectively between the sliding valve hole 42 at the outlet side plunger hole 41 and the outlet side of each group.

At this moment; On the axial direction of input shaft 2, wear intercommunicating pore 43,43... in the position of the substantial middle that becomes cylinder body 7; Intercommunicating pore 43,43... regularly are communicated with outlet side plunger hole 41 and outlet side with the shortest between the axle center of sliding valve hole 42, more tilt than radial direction.

In the present embodiment, same with the formation method of said intercommunicating pore 33,33..., intercommunicating pore 43,43 is also adopted the method for using the shell core to form when the casting.

In addition, as the diameter outlet side of the interflow portion 46 of the interflow portion of intercommunicating pore 43,43... and outlet side plunger hole 41,41... regularly the internal diameter hole enlargement of sliding valve hole 42 form.Through such formation; When regularly the wide diameter portion 11a of guiding valve 11 interdicts outlet side plunger hole 41 with input side grease chamber 35 and outlet side grease chamber 45 by outlet side (neutral position); Can prevent that owing to the periphery to wide diameter portion 11a acts on hydraulic pressure equably outlet side regularly guiding valve 11 is pressed to the specific circumferencial direction as the inside of outlet side timing sliding valve hole 42.

Extremely shown in Figure 8 like Fig. 6; See from the axial direction of input shaft 2; Input side plunger hole 31,31... and outlet side plunger hole 41,41... with uniformly-spaced mutual in abutting connection with (that is, on the concentric circle that with through hole 7c is the center by input side plunger hole 31 → outlet side plunger hole 41 → input side plunger hole 31 → outlet side plunger hole 41 → ... the order assortment).

In addition; See from the axial direction of input shaft 2 equally; Input side regularly sliding valve hole 32,32... and outlet side regularly sliding valve hole 42,42... with uniformly-spaced mutual in abutting connection with (that is, on the concentric circle that with through hole 7c is the center by input side regularly sliding valve hole 32 → outlet side regularly sliding valve hole 42 → input side regularly sliding valve hole 32 → outlet side regularly sliding valve hole 42 → ... the order assortment).In addition, the center of the cylinder body 7 between input side plunger hole 31 and outlet side plunger hole 41 (through hole 7c) side configuration input side timing sliding valve hole 32 or outlet side timing sliding valve hole 42.

Like Fig. 7 and shown in Figure 8, on the inner peripheral surface of the through hole 7c of cylinder body 7, form two place's internal circle grooves altogether of forming by first internal circle groove and second internal circle groove.This internal circle groove forms ring-type at the Zhou Fangxiang of inner peripheral surface, and all regularly sliding valve hole 32,32... and outlet side timing sliding valve hole 42,42... are communicated with arbitrary internal circle groove with input side.

In addition; In the explanation afterwards by the space that outer circumferential face surrounds of near first internal circle groove the input side end face 7a and input shaft 2 as input side grease chamber 35, by the space of the outer circumferential face encirclement of near second internal circle groove the outlet side end face 7b and input shaft 2 as outlet side grease chamber 45.

In addition, be housed in the present embodiment input side plunger 8 in the cylinder body 7, input side regularly guiding valve 9, outlet side plunger 10, outlet side regularly the number of guiding valve 11 be respectively seven, but be not limited thereto, so long as a plurality ofly just can receive same effect.

Promptly; Hyaulic infinite variable speed mechanism 1 has disposed input side plunger 8,8... on input shaft 2; Outlet side plunger 10,10...; Taken in each regularly cylinder body 7 of guiding valve 9,9... and 11,11... abreast with axial direction free sliding; With the input side swash plate 6 of the front end butt of input side plunger 8,8..., with the outlet side swash plate 12 of these input side swash plate 6 opposition sides and said outlet side plunger 10,10... butt, in this Hyaulic infinite variable speed mechanism 1; Be configured on the same radius of cylinder body 7, make many mutual configurations of each plunger hole 31,31... and 41, the 41... that take in input side plunger 8,8... and outlet side plunger 10,10..., the central side between input side plunger hole 31,31... and outlet side plunger hole 41,41... is provided with each regularly sliding valve hole 32,32... and 42,42....

Thus, can guarantee to accommodate each plunger hole 31,31... and 41, the 41... of each plunger 8,8... and 10,10... and accommodate each regularly each wall thickness between sliding valve hole 32,32... and 42, the 42... and make cylinder body 7 miniaturizations regularly of guiding valve 9,9... and 11,11....In addition; When not changing the boundary dimension of cylinder body 7; Can make each plunger hole 31,31... and 41, the 41... that accommodates each plunger 8,8... and 10,10... and accommodate each regularly guiding valve 9,9... and 11,11... each regularly the bore of sliding valve hole 32,32... and 42,42... become big, can easily carry out the processing in hole.

Below, using Fig. 1, Fig. 2, Fig. 6 and Fig. 7 are to the input side plunger 8 of a mode of execution of first plunger of hydraulic pressure installation of the present invention, and the outlet side plunger 10 of a mode of execution of second plunger of hydraulic pressure installation of the present invention is elaborated.

In addition, input side plunger 8 and outlet side plunger 10 be owing to same shape is made in the parts generalization in the present embodiment, but be not limited thereto, and input side plunger 8 also can be according to pump capacity and capacity motor etc. with different shapes, number formation with outlet side plunger 10.

Like Fig. 1 and shown in Figure 2, input side plunger 8 is the parts that become the rotating drive force transformation of input shaft 2 pressure of the hydraulic oil in the oil hydraulic circuit that in cylinder body 7, forms.In addition, outlet side plunger 10 is the parts that are transformed into the pressure of the hydraulic oil in the oil hydraulic circuit that in cylinder body 7, forms the rotating drive power of outlet side swash plate 12.

In addition, like Fig. 1, Fig. 6 and shown in Figure 7, input side plunger 8,8... are housed among input side plunger hole 31, the 31..., and outlet side plunger 10,10... are housed among outlet side plunger hole 41, the 41....

As shown in Figure 1, outlet side plunger 10 mainly is made up of plunger portion 10a, ball 10b, butt dish 10c etc.

Plunger portion 10a is the parts of general cylindrical shape, can slip with the outlet side plunger hole 41 of cylinder body 7 and to-and-fro motion.Ball 10b is roughly spherical parts, fixedly installs integratedly with the butt dish 10c of disc-shaped part roughly.Butt dish 10c is attached at the protruding terminus (specific output side end face 7b is to the end of the outstanding side of outlet side swash plate 12) of plunger portion 10a swingably by ball 10b; Simultaneously; The protruding terminus of plunger portion 10a (is said with ball 10b is inaccessible tightlyer; On ball 10b and butt dish 10c, wear the lubrication oil road, the each a small amount of bearing surface from this lubrication oil road direction butt dish 10c and outlet side swash plate 12 of the hydraulic oil in the outlet side plunger hole 41 spills lubricated this bearing surface).

Accommodating spring bumper cover 29 and spring 30 in the inside of plunger portion 10a.Spring 30 one of which ends and spring bumper cover 29 butts, the other end is connected on the diapire face of outlet side plunger hole 41 from the opening end of plunger portion 10a is outstanding.Therefore, outlet side plunger 10 by spring 30 to from the outstanding direction of the outlet side end face 7b of cylinder body 7 (that is, butt dish 10c is connected to the direction on the swash plate face 12a of the outlet side swash plate 12) application of force.

In addition, input side plunger 8 also mainly is made up of plunger portion, ball, butt dish etc., forms the structure same with said outlet side plunger 10.In addition, accommodate spring bumper cover and spring in the inside of plunger portion, an end of spring and spring bumper cover butt, the other end is connected on the wall of input side plunger hole 31 from the opening end of plunger portion is outstanding.Therefore, input side plunger 8 by spring to from the outstanding direction of the input side end face 7a of cylinder body 7 (that is, the butt dish is connected to the direction on the swash plate face 6a of the input side swash plate 6) application of force.

Below, specify the input side guiding valve 9 regularly of a mode of execution of first guiding valve of hydraulic pressure installation of the present invention with Fig. 1 and Fig. 9 and even Figure 12, and the outlet side of a mode of execution of second guiding valve of hydraulic pressure installation of the present invention guiding valve 11 regularly.

In addition, as shown in Figure 9, the guiding valve 9 of input side timing is in the present embodiment made same shape with outlet side timing guiding valve 11 for the parts generalization, but is not limited thereto, and input side regularly guiding valve 9 also can be made different shapes with outlet side timing guiding valve 11.

Like Fig. 9 and shown in Figure 10, input side regularly guiding valve 9 is the parts that switch in the stream of the hydraulic oil of coming in and going out in the input side plunger hole 31 of accommodating input side plunger 8.The parts that input side timing guiding valve 9 has the different substantial cylindrical of external diameter mainly are made up of wide diameter portion 9a, wide diameter portion 9b, 9b, the 9c of valve shaft portion, 9c and engagement portion 9d etc.

Wide diameter portion 9a and wide diameter portion 9b, 9b are the positions of substantial cylindrical, and its external diameter is roughly the same with the internal diameter of the input side timing sliding valve hole 32 that on cylinder body 7, forms.Therefore, wide diameter portion 9a and wide diameter portion 9b, the relative input side timing of 9b sliding valve hole 32 can slip and to-and-fro motion airtightly.In addition, the periphery at wide diameter portion 9b, 9b suits to form groove.

Wide diameter portion 9a is configured in regularly intermediate portion (or the substantial middle portion) configuration of the long side direction (reciprocating direction) of guiding valve 9 of input side.In addition, wide diameter portion 9b, 9b are positioned at the regularly two ends of the long side direction of guiding valve 9 of input side.

The 9c of valve shaft portion is the position than wide diameter portion 9a and wide diameter portion 9b, substantial cylindrical that the 9b external diameter is little, between wide diameter portion 9a and wide diameter portion 9b, 9b.

Engagement portion 9d gives prominence to setting from a side wide diameter portion 9b towards the long side direction of input side timing guiding valve 9.The joint of engagement portion 9d and wide diameter portion 9b is a collapsed shape, is fastened on the input side guiding valve cam 37.

In the present embodiment, engagement portion 9d is formed analyse and observe roughly abacus pearl,, improve the making property reducing with when the surface of contact that engages the place of the slot part 37a of input side guiding valve cam 37 is pressed.In addition, engagement portion 9d also can form analyse and observe roughly circular-arc.

Like Figure 11, shown in Figure 12, input side regularly guiding valve 9 becomes from the mode of the outstanding direction of the input side end face 7a of cylinder body 7 with engagement portion 9d, is inlaid in slidably in the input side timing sliding valve hole 32.

For the wide diameter portion 9b that is connected on the 9d of engagement portion; Even input side regularly guiding valve 9 in regularly to-and-fro motion in the sliding valve hole 32 of input side, also always than the connection part that is communicated with the input side grease chamber 35 that forms by first internal circle groove and input side timing sliding valve hole 32 in more by input side end face 7a side.In addition; For 9d wide diameter portion 9b far away from the engagement portion; Even input side regularly guiding valve 9 in regularly to-and-fro motion in the sliding valve hole 32 of input side, also always than the connection part that is communicated with the outlet side grease chamber 45 that forms by second internal circle groove and input side timing sliding valve hole 32 in more by outlet side end face 7b side.

And then wide diameter portion 9a is configured in and is communicated with the regularly corresponding position of the interflow portion that is connected oil circuit (intercommunicating pore 33) and input side timing sliding valve hole 32 36 of sliding valve hole 32 of input side plunger hole 31 and input side.At this moment, the external diameter of the internal diameter constituent ratio wide diameter portion 9a of interflow portion 36 is big, and the length of the interflow portion 36 on the long side direction (reciprocating direction) of formation input side timing guiding valve 9 and the same length of wide diameter portion 9a.

Therefore; Shown in figure 12; Wide diameter portion 9a is through regularly guiding valve 9 slip in input side timing sliding valve hole 32 of input side; Can take the position of (1) blocking input side grease chamber 35 and input side plunger hole 31, connection outlet side grease chamber 45 and input side plunger hole 31; (2) interdict the position of all input side grease chambeies 35 and outlet side grease chamber 45 and input side plunger hole 31, (3) are communicated with the position of input side grease chamber 35 and input side plunger hole 31, blocking outlet side grease chamber 45 and input side plunger hole 31, and it counts three positions.

In addition, like Fig. 9 or shown in Figure 10, the wide diameter portion 9a of input side timing guiding valve 9 partly forms notch part 9e for input side grease chamber 35 and 45 both sides of outlet side grease chamber (promptly to high pressure side, low voltage side both sides) of this wide diameter portion 9a at cylindric shoulder.

But the shape of notch part 9e is restriction not.

Thus, when input side plunger hole 31 is communicated with input side grease chamber 35 or outlet side grease chamber 45, switch moment at initial stage, just can suppress the pulsation generation that causes by the rapid variation in pressure in the oil circuit through making small hydraulic oil stream at oil circuit.In addition, can reduce the noise that input side takes place when regularly guiding valve 9 moves.

In addition; Input side regularly the length relation of length and the wide diameter portion 9a of the interflow portion 36 of the long side direction of guiding valve 9 owing to come suitably to select, so be not limited to the situation of same length of length and the wide diameter portion 9a of the interflow portion 36 of the long side direction of formation input side timing guiding valve 9 as present embodiment according to the drive performance of hydraulic pressure installation of the present invention.That is, on the long side direction of input side timing guiding valve 9, both can make interflow portion 36 longer than wide diameter portion 9a, also can be shorter than wide diameter portion 9a.

Below use Fig. 1, Fig. 3, Figure 12 to Figure 17 specifies the input side guiding valve cam 37 as the main portion of the present invention.

To shown in Figure 17, input side guiding valve cam 37 is druum cam parts of roughly ring-type like Figure 12, analyses and observe in the outer circumferential face formation of this ring to be roughly circular-arc slot part 37a.

In addition; Input side guiding valve cam 37 forms recess 37b, the 37b of two opposite side distance of separations (two width of cloth) shape that is parallel to each other in the inner peripheral surface side; Like Fig. 3 or shown in Figure 4, formation engages, can not relatively rotate ground axle suspension with protuberance 4s, the 4s of the two opposite side distance of separation shapes that are parallel to each other that on the lug boss 4r of input side housing 4, form.

Thus, as shown in Figure 1, can easily can not relatively rotate ground axle suspension input side guiding valve cam 37 with input side housing 4, can make cylinder body 7 consistent really with the action phase place of input side guiding valve cam 37.

And then to shown in Figure 17, input side guiding valve cam 37 is formed on the inner peripheral surface side three recess 37c that prevent wrong installation usefulness different with recess 37b, the 37b of said two opposite side distance of separation shapes like Figure 12.In addition, constitute with the 3rd protuberance 4t that on the lug boss 4r of Fig. 3 or input side housing 4 shown in Figure 4, forms and engage.

Thus, the direction chimeric owing to the ability of input side guiding valve cam 37 and input side housing 4 is certain, so can prevent the fault that the mistake of installation and so on is installed under the state of phase phase difference 180 degree by error.

In addition; Extremely shown in Figure 17 like Figure 12; Slot part 37a forms the sinusoidal wave shape of a continuous amplitude; The said engagement portion 9d of engaging in this slot part 37a rotates between one-period at the periphery upper edge of input side guiding valve cam 37 slot part 37a at input side timing guiding valve 9, and this input side regularly guiding valve 9 regularly reciprocatingly slides once sliding valve hole 32 inside at input side.

At this moment, shown in figure 17, the section shape of said engagement portion 9d constitutes the abacus pearlitic texture, and chimeric part forms circular arc or curve form.In addition, the section shape of slot part 37a also constitutes circular-arc to the bulging of groove private side of the side that erects from the bottom.Like this and since said engagement portion 9d with analyse and observe the contact that is roughly circular-arc slot part 37a and can reduce surface of contact and press, so can drive regularly guiding valve 9 of input side smoothly.

Below specify the outlet side guiding valve 11 regularly of a mode of execution of second guiding valve of hydraulic pressure installation of the present invention with Fig. 1 and Fig. 9 to Figure 12.

Like Fig. 9 and shown in Figure 10, outlet side regularly guiding valve 11 is parts of replacement stream of the hydraulic oil of discrepancy in accommodating the outlet side plunger hole 41 of outlet side plunger 10.Outlet side timing guiding valve 11 has the parts of the different substantial cylindrical shape of external diameter, mainly is made up of wide diameter portion 11a, wide diameter portion 11b, 11b, the 11c of valve shaft portion, 11c and engagement portion 11d etc.

Wide diameter portion 11a and wide diameter portion 11b, 11b are the positions of substantial cylindrical, and its external diameter is roughly the same with the internal diameter of the outlet side timing sliding valve hole 42 that on cylinder body 7, forms.Therefore, wide diameter portion 11a and wide diameter portion 11b, 11b relatively outlet side regularly sliding valve hole 42 slip airtightly and to-and-fro motion.

Wide diameter portion 11a is in regularly intermediate portion (or the substantial middle portion) configuration of the long side direction (reciprocating direction) of guiding valve 11 of outlet side.In addition, wide diameter portion 11b, 11b are positioned at two ends on the long side direction of outlet side timing guiding valve 11.

The 11c of valve shaft portion is the position than wide diameter portion 11a and wide diameter portion 11b, substantial cylindrical that the 11b external diameter is little, between wide diameter portion 11a and wide diameter portion 11b, 11b.

Engagement portion 11d gives prominence to setting from a side wide diameter portion 11b to the long side direction of outlet side timing guiding valve 11.The joint of engagement portion 11d and wide diameter portion 11b is a collapsed shape, engages with outlet side guiding valve cam 47.

In the present embodiment, regularly guiding valve 9 is same with input side, and engagement portion 11d forms and analyses and observe roughly abacus pearl, makes low with the surface of contact pressure drop that engages the place of outlet side guiding valve cam 47.In addition, engagement portion 11d also can form analyse and observe for roughly circular-arc.

That is, be located at each regularly engagement portion 9d, the 11d of the front end of guiding valve 9,11 constitute to analyse and observe and be straight line shape, thus, can carry out each regularly processing of guiding valve 9,11 easily.In addition, each timing guiding valve 9,11 is slided smoothly.

Shown in figure 11, outlet side regularly guiding valve 11 is inlaid in the outlet side timing sliding valve hole 42 slidably, so that engagement portion 11d becomes the outstanding direction from the outlet side end face 7b of cylinder body 7.

For the wide diameter portion 11b that is connected on the 11d of engagement portion; Even regularly guiding valve 11 is in regularly to-and-fro motion in the sliding valve hole 42 of outlet side for outlet side, the joint that also often is positioned at than is communicated with the outlet side grease chamber 45 that formed by second internal circle groove and outlet side timing sliding valve hole 42 is more by outlet side end face 7b side.In addition; Wide diameter portion 11b for a 11d side far away from the engagement portion; Even regularly guiding valve 11 is in regularly to-and-fro motion in the sliding valve hole 42 of outlet side for outlet side, the joint that also often is positioned at than is communicated with the input side grease chamber 35 that formed by first internal circle groove and outlet side timing sliding valve hole 42 is more by input side end face 7a side.

And then wide diameter portion 11a is configured in and connects the regularly corresponding position of interflow portion 46 of sliding valve hole 42 of oil circuit (intercommunicating pore 43) and outlet side, and this connects oil circuit and is communicated with outlet side plunger hole 41 and outlet side timing sliding valve hole 42.At this moment, the external diameter of the internal diameter constituent ratio wide diameter portion 11a of interflow portion 46 is big, and the length of the interflow portion 46 on the long side direction (reciprocating direction) of formation outlet side timing guiding valve 11 and the same length of wide diameter portion 11a.

Therefore; Shown in figure 12; Wide diameter portion 11a is through regularly guiding valve 11 slip in outlet side timing sliding valve hole 42 of outlet side; Can take the position of (1) blocking input side grease chamber 35 and outlet side plunger hole 41, connection outlet side grease chamber 45 and outlet side plunger hole 41; (2) interdict the position of all input side grease chambeies 35 and outlet side grease chamber 45 and outlet side plunger hole 41, (3) are communicated with the position of input side grease chamber 35 and outlet side plunger hole 41, blocking outlet side grease chamber 45 and outlet side plunger hole 41, and it counts three positions.

In addition, like Fig. 9 or shown in Figure 10, same with the wide diameter portion 9a of said input side timing guiding valve 9, the outlet side regularly wide diameter portion 11a of guiding valve 11 partly forms notch part 11e at the cylindric shoulder of this wide diameter portion 11a.Thus, can be reduced in the noise that outlet side takes place when regularly guiding valve 11 moves.

In addition; Because the outlet side regularly relation of the length of length and the wide diameter portion 11a of the interflow portion 46 of the long side direction of guiding valve 11 is suitably selected according to the drive performance of hydraulic pressure installation of the present invention, so be not limited to the situation of same length of length and the wide diameter portion 11a of the interflow portion 46 of the long side direction of formation outlet side timing guiding valve 11 as present embodiment.That is, on the long side direction of outlet side timing guiding valve 11, both can make interflow portion 46 longer than wide diameter portion 11a, also can be shorter than wide diameter portion 11a.

Below use Fig. 1, Fig. 3, Figure 12 to Figure 17 specifies the outlet side guiding valve cam 47 as major component of the present invention.

To shown in Figure 17, outlet side guiding valve cam 47 is druum cam parts of roughly ring-type like Figure 12, on the outer circumferential face of this ring, forms to analyse and observe to be roughly circular-arc slot part 47a.

In addition; Outlet side guiding valve cam 47 is the same with input side guiding valve cam 37; Form recess 47b, the 47b of the two opposite side distance of separation shapes that are parallel to each other in the inner peripheral surface side; Constitute with protuberance 12d, the 12d of the two opposite side distance of separation shapes that are parallel to each other that on the front end of the holding part 12b of outlet side swash plate 12, form and engage, can not relatively rotate by the axle supporting.

Thus, as shown in Figure 1, can easily can not relatively rotate ground axle suspension outlet side guiding valve cam 47 with outlet side swash plate 12, can make cylinder body 7 consistent really with the phase place of outlet side guiding valve cam 47.

Promptly; On input side housing 4 and outlet side swash plate 12, form the protuberance 4m and the 12d of two opposite side distance of separation shapes at axle support inner face, and on each guiding valve cam 37,47; Form recess 37b, the 47b of two opposite side distance of separation shapes in axle support outside; Said protuberance 4m and 12d are engaged with said recess 37b, 47b, make input side housing 4 and input side swash plate 12 become the structure that can not fixedly install rotationally each other, thus with each guiding valve cam 37,47; Can make cylinder body 7 consistent really, can obtain the timing that oil circuit switches really with the phase place of each timing guiding valve 9,11.In addition, installation exercise can easily carry out.

And then; Extremely shown in Figure 17 like Figure 12; Outlet side guiding valve cam 47 the inner peripheral surface side form recess 47b, 47b with said two opposite side distance of separation shapes different prevent wrong the 3rd recess 47c that usefulness is installed, formation engages with the 3rd protuberance 12e that on the front end of the holding part 12b of input side swash plate 12, forms.

Thus, the direction chimeric owing to the ability of outlet side guiding valve cam 47 and outlet side swash plate 12 is certain, so can prevent the fault that the mistake of installation and so on is installed under the state of phase phase difference 180 degree by error.

Promptly; On input side housing 4 and outlet side swash plate 12; At protuberance 4m and 12d different three protuberance 4n and the 12e of axle support inner face formation, and on each guiding valve cam 37,47, form three recess 37c, the 47c different with recess 37b, the 47b of said two opposite side distance of separations in axle support outside with said two opposite side distance of separation shapes; Make the 3rd protuberance 4n and 12e and the 3rd recess 37c, 47c engaging; Make the structure that can not fixedly install input side housing 4 and outlet side swash plate 12c and each guiding valve cam 37,47 with relatively rotating, thus, can prevent that the mistake when Hyaulic infinite variable speed mechanism 1 is installed from installing.In addition, can easily carry out installation exercise.

In addition; Extremely shown in Figure 17 like Figure 12; Slot part 47a forms the sinusoidal wave shape of a continuous amplitude; The said engagement portion 11d of engaging in this slot part 47a rotates between one-period at the periphery upper edge of outlet side guiding valve cam 47 slot part 47a at outlet side timing guiding valve 11, and this outlet side regularly guiding valve 11 regularly reciprocatingly slides once sliding valve hole 42 inside at outlet side.

At this moment, since at said engagement portion 11d with to analyse and observe the contact place surface of contact pressure drop that is roughly circular-arc slot part 47a low, so can drive regularly guiding valve 11 of outlet side smoothly.

Promptly; Hyaulic infinite variable speed mechanism 1 disposes input side plunger 8, outlet side plunger 10 on input shaft 2; Taken in each regularly cylinder body 7 of guiding valve 9,11 abreast with axial direction free sliding; With the input side swash plate 6 of the front end butt of input side plunger 8, at the outlet side swash plate 12 of these input side swash plate 6 opposition sides and said outlet side plunger 10 butts, in said Hyaulic infinite variable speed mechanism 1; Be fixed in each slot part 37a, the 47a that each timing guiding valve 9,11 1 end of engaging are set on each guiding valve cam 37,47 of input side housing 4 sides or outlet side swash plate 12 sides; Analysing and observe for circular-arc, thus, can prevent each regularly sintering of guiding valve 9,11 with the abutting part of the engagement portion 9d of the front end of guiding valve 9,11, the 11d formation that is located at respectively regularly of this slot part 37a, 47a.In addition, each timing guiding valve 9,11 is successfully slided.

Below use Fig. 1, Fig. 2, Figure 18 to Figure 20 specify second swash plate as present embodiment, as the outlet side swash plate 12 of major component of the present invention.

Outlet side swash plate 12 is making outlet side plunger 10 reciprocating power (i.e. the pressure of hydraulic oil in the oil hydraulic circuit of formation cylinder body 7 in) be transformed into the parts of the rotating drive power of output shaft etc.

Like Fig. 1 or shown in Figure 180, outlet side swash plate 12 is the parts that are provided with the general cylindrical shape shape of the through hole that connects input shaft 2 (saying the outer lining 50 on the input shaft 2 that is embedded in) tightly, is provided with swash plate face 12a in its front portion.Swash plate face 12a is the plane, and the protruding terminus of outlet side plunger 10 (butt dish 10c) is connected on the swash plate face 12a.The axis of the relative input shaft 2 of swash plate face 12a becomes the tilt angle (angle that the axis of swash plate face 12a and input shaft 2 forms) of regulation.

Like Fig. 1 or shown in Figure 2, the rear end of outlet side swash plate 12 is fixing with output shell 48, makes outlet side swash plate 12 and output shell 48 unitary rotation.In addition; Owing to be embedded the outer ring of outlet side tapered roller bearing 51 in the through hole rear end of outlet side swash plate 12; Outlet side swash plate 12 between the through hole of outlet side swash plate 12 and lining 50, clamps outlet side needle roller bearing 52, so can relatively rotate with input shaft 2.

To shown in Figure 20, outlet side swash plate 12 is cast aluminium system in the present embodiment, can seek big lightweight like Figure 18.In addition, dispose a plurality of stiffening ribs 49, guarantee to tolerate rigidity from the butt power of outlet side plunger 10,10... at the peripheral part of outlet side swash plate 12.

In addition, like Figure 19 or shown in Figure 20, stiffening rib 49 is parallel with input shaft 2, and it is parallel to each other to constitute 49 a plurality of of each stiffening ribs.That is, muscle is not with radial outstanding.

The interval of stiffening rib 49 makes and the roughly inversely proportional configuration of distance of the face (the for example outlet side end face 7b of cylinder body 7) of swash plate face 12a and input shaft 2 quadratures apart.

That is, be formed in the part closer with the distance of outlet side end face 7b (the for example part of the downside among Figure 20), the interval of stiffening rib 49 is wide, and with the part (the for example part of the upside among Figure 20) of the distance of outlet side end face 7b, the interval of stiffening rib 49 is narrow.In other words, the interval of stiffening rib 49 length of being arranged to the axis direction of relative outlet side swash plate 12 is inversely proportional to.The interval that promptly constitutes the long part stiffening rib 49 of the length of axis direction of outlet side swash plate 12 is wide, and the interval of the shorter then stiffening rib 49 of the length of the axis direction of outlet side swash plate 12 is narrow more.

Promptly; Hyaulic infinite variable speed mechanism 1 has disposed input side plunger 8 on input shaft 2, outlet side plunger 10 has been taken in each regularly cylinder body 7 of guiding valve 9,11 abreast with axial direction free sliding; Input side swash plate 6 with the front end butt of input side plunger 8; Be positioned at these input side swash plate 6 opposition sides, with the outlet side swash plate 12 of said outlet side plunger 10 butts, in said Hyaulic infinite variable speed mechanism 1, at the periphery of outlet side swash plate 12 and input shaft 2 a plurality of stiffening ribs 49 that laterally arrange; Constitute the interval of this stiffening rib 49 of configuration; Make it consistent, thus, can make 12 lightweights of outlet side swash plate with the distance of leaving with rectangular of the axle center of outlet side swash plate 12.In addition, can improve rotation precision (dynamic balancing).In addition, make the making of input side swash plate 12 become easy.

And then, on stiffening rib 49, form protuberance 49a, be arranged to make the length of axis direction of size and the outlet side swash plate 12 of this protuberance 49a to be inversely proportional to.That is, the long part of length that constitutes the axis direction of outlet side swash plate 12 constitutes protuberance 49a lessly, and the size of the shorter then protuberance of the length of the axis direction of outlet side swash plate 12 49a is big more.In the present embodiment, this protuberance 49a from the outstanding part of the length of the outer circumferential face of outlet side swash plate 12 as protuberance 49a, make from swash plate face 12a differently with the length of axis parallel prolongation, make dimensional changes.But the different formation of size of making protuberance 49a does not limit in the present embodiment, also can make with swash plate face 12a before and after the stiffening rib 49 of opposition side become big, middle part becomes big before and after also can making.

That is, make the width of stiffening rib 49 and leave and the consistent structure of distance in rectangular of the axle center of input side swash plate 12, thus, guarantee also can realize lightweight to the compression strength of the axial direction of input side swash plate 12.In addition, owing to can adjust balance through cutting down stiffening rib 49, the adjustment balanced operation becomes easy.

In addition, in order to change the weight of stiffening rib 49, also can be the structure that changes the width of stiffening rib 49.That is, the length that also can constitute with the axis direction of outlet side swash plate 12 is inversely proportional to, and the thickness of the longer then stiffening rib 49 of the length of axis direction is thin more, the shorter then thick more structure of the length of axis direction.Like this, rigidity can be guaranteed effectively, weight balancing and rotary balance can be obtained.

In addition, shown in figure 19, stiffening rib 49 constitute parallel with input shaft 2 and comprise relatively top dead center A and lower dead center B on the swash plate face 12a face, on the face parallel, give prominence to vertical Tilt Datum Plane face C.

Thus, in the stripping operation when casting, can pull out, can make outlet side swash plate 12 be cast aluminium system to certain orientation.In addition, casting manipulations also becomes easy.

That is, stiffening rib 49 make parallel with center of rotation and with the face of the Tilt Datum Plane line parallel of input side swash plate 12 on outstanding structure, thus, can constitute by aluminum mo(u)lding (cast aluminium).In addition, casting manipulations becomes easy.

In addition, in the present embodiment, use fixedly swash plate as outlet side swash plate 12, but also can adopt movable swash plate as outlet side swash plate 12.

In addition, outlet side swash plate 12 is because the relative axis of output shaft 2 axisymmetric not, so the dynamic balancing (weight balancing and rotary balance) when must adjustment rotating.Outlet side swash plate 12 shown in the present embodiment has stiffening rib 49, through prune this stiffening rib 49 and adjusting of part, can carry out dynamically balanced adjustment with comparalive ease.

Below specify non-return safety valve 38a, the 38b of present embodiment with Fig. 1 and Figure 21.In Figure 21, what represent with the circle that is positioned at paper left side is the input side hydraulic pressure installation, and what represent with the circle that is positioned at the right side is the outlet side hydraulic pressure installation.In addition, the mobile usefulness of the hydraulic oil during acceleration clockwise rotates to be represented, is through input side hydraulic pressure installation, input side grease chamber 35, outlet side hydraulic pressure installation and outlet side grease chamber 45, returns flowing of input side hydraulic pressure installation afterwards again.The mobile usefulness of the hydraulic oil during deceleration rotates counterclockwise to be represented, is to turn back to flowing of input side grease chamber 35 through input side hydraulic pressure installation, outlet side grease chamber 45, outlet side hydraulic pressure installation.

Like Fig. 1 or shown in Figure 21; Non-return safety valve 38a, 38b are provided in a side of the parts that one constitutes on the supply path of the hydraulic oil that makes action such as said each plunger 8,10; Have the function of the safety check that prevents the hydraulic oil adverse current simultaneously and become the function of discharging the safety valve of hydraulic oil below the specified value, according to the pressure in the hydraulic path for pressure in the hydraulic path is risen.

In the present embodiment; To be communicated with the mode in input side grease chamber 35 and outlet side grease chamber 45 respectively; Correspondence is provided with two non-return safety valve 38a, 38b respectively; At the wide diameter portion of input shaft 2, with both sides' non-return safety valve 38a, 38b on right angle orientation parallel towards, and be provided with mode with the orthogonal axe of input shaft 2.

Thus, Hyaulic infinite variable speed mechanism 1 can become miniaturization, simultaneously, is communicated with oil circuit 2b on the axis of input shaft 2, can simplify hydraulic path.

In addition; In the present embodiment; The exhaust port of the hydraulic oil when making performance as the function of safety valve is connected on the oil circuit 2b in the supply path (first side of safety check) as hydraulic oil; When the safety valve function action, do not have the problem of not appending supply hydraulic oil, and the capacity of the supply pump 26 used of hydraulic oil supply can be done for a short time.

More than, explain that the integral body of the Hyaulic infinite variable speed mechanism 1 of one embodiment of the invention constitutes.

Then, to relating to one embodiment of the invention, the angular adjustment action of the input side swash plate 6 that is produced by the hydraulic servomechanism 3 as the control device that is used to change output speed describes with Fig. 1 to Fig. 4 and Figure 22 to Figure 25.

In Fig. 1 to Fig. 4 and Figure 22 to Figure 25, as previously mentioned, abreast at fore-and-aft direction configuration power piston 15, the rear end of this power piston 15 is connected an end of input side swash plate 6 at the top of cartridge housing body 4a and input shaft 2., on this feedback pilot valve 14, be connected at above-below direction, dispose servo guiding valve 13 and feedback pilot valve 14 up and down at the sidepiece of this power piston 15 by feedback link 24 and input side swash plate 6.

In such formation, said servo guiding valve 13 by the ratio adjustment valve 25 that electromagnetic proportional valve constitutes, can make the hydraulic pressure of discharging from this ratio adjustment valve 25 change through control, is sliding up and down and displacement.Corresponding to the position of this servo guiding valve 13, can switch to grease chamber, front side 17 and transport the pressure oil from supply pump 26, first form (A position) that rear side grease chamber 18 is communicated with hydraulic pressure oil tank 27; Grease chamber, front side 17 is communicated with hydraulic pressure oil tank 27, transports second form (B position) from the pressure oil of supply pump 26 to rear side grease chamber 18; The oil circuit 4i of grease chamber, front side 17 and rear side grease chamber 18, the 3rd form (neutral position) of 4h are led in obstruction.

At this moment, constitute according to each form power piston 15 front and back and slide, being associated with this action rotates input side swash plate 6, to should rotation angle, makes feedback pilot valve 14 displacements by feedback link 24 in addition.

In addition, the displacement of making feedback pilot valve 14 passes to servo guiding valve 13 through spring members 20, the angle of feedback input side swash plate 6.

That is, constitute corresponding output and compensate, make input side swash plate 6 carry out specified action from ratio adjustment valve 25.

Like Fig. 4, shown in Figure 22, in said first form (promptly; Grease chamber, top 40 and grease chamber, bottom 44 are communicated with by the second diameter reducing part 13d, and by the form that the oil circuit 13m from the first diameter reducing part 13n is communicated with connection mouth 4q, servo guiding valve 13 is in the A position) in; Be communicated with through the grease chamber, top 40 and the second diameter reducing part 13d; In grease chamber, said front side 17, transport hydraulic oil from supply pump 26, the hydraulic oil hydraulic return oil tank 27 in the rear side grease chamber 18, power piston 15 rearward slides.

In addition, shown in figure 23, in said second form (promptly; Grease chamber, top 40 is communicated with oil circuit 4h through the second diameter reducing part 13d, and grease chamber, bottom 44 is through the 3rd diameter reducing part 13f, the form that oil circuit 13p, 13m are communicated with connection mouth 4q; Servo guiding valve 13 is in the B position) in, be communicated with through grease chamber, top 40 and oil circuit 4h, in said rear side grease chamber 18, supply with the hydraulic oil of self-pumping 26; Hydraulic oil in the grease chamber, said front side 17 turns back to hydraulic pressure oil tank 27, and power piston 15 forwards slides.

In addition, shown in figure 24, in said the 3rd form (that is, grease chamber, top 40 and grease chamber, bottom 44 and other disconnected forms such as grease chamber, neutral position), the positions that power piston 15 keeps at that time.

To shown in Figure 24, be located at the fixing fixing part 6c of input side swash plate 6 of fixed component 16 of the front end of power piston 15 like Figure 22, corresponding said three forms, making fixing part 6c roughly, fore-and-aft direction moves also rotating drive input side swash plate 6.At this moment, owing to make the structure that fixing part 6c can slide at above-below direction along the inner wall part of コ word shape, can be absorbed in the displacement of the above-below direction of the fixing part 6c that produces when input side swash plate 6 rotates.

Through such formation, formation is associated with the reciprocatingly sliding of fore-and-aft direction of power piston 15, and input side swash plate 6 back and forth rotates.

In addition, in the swash plate face 6a of input side swash plate 6, in retraction stroke in (during pump) or the compression stroke in the scope (high pressure side) of input side plunger 8 butts of (during motor), the high pushing force that effect is produced by input side plunger 8.

To this, the scope (low voltage side) of input side plunger 8 butts in retraction stroke is compared the low pushing force of only effect with the pushing force that input side plunger 8 from said expansion stroke receives.

In the Hyaulic infinite variable speed mechanism 1 of present embodiment, constituting towards vehicle direct of travel and left side is the high pressure side, and the right side is a low voltage side.

Therefore, become the axis of the relative input shaft 2 of said fixing part 6c, the structure of (that is high pressure side) bias configuration in the left side.

That is, make and considered not encourage structure by the uneven butt power moment that cause, that input side swash plate 6 receives of input side plunger 8,8....

Thus, can alleviate the uneven stress of the pivotal bearing part that is added in input side swash plate 6, the rotation of input side swash plate 6 is carried out smoothly.

Promptly; Make the center of rotation of the cylinder body 7 of power piston 15 through accommodating input side plunger 8, compare and rectangular of the center of rotation of input side swash plate 6, input side plunger 8 bias configuration are in the side with the high pressure butt; Thus, can prevent on input side swash plate 6, to apply unsuitable stress.In addition, input side swash plate 6 is successfully rotated.

Feedback link 24 is flat steel plate member mades, and with said power piston 15 almost parallels configuration, rotation freely is supported in an end of long side direction on the axle 55 that the left surface of cartridge housing body 4a is given prominence to, and constitutes the fulcrum of link mechanism.In addition,, form the notch part 24a that makes the open roughly U font in rear, the outstanding lever pin 6d that is provided with of fixing left, constitute the force of link mechanism to input side swash plate 6 at the other end of the long side direction of feedback link 24.At this, though follow the rotation of input side swash plate 6, the distance between fulcrum-force changes, and through on notch part 24a, having play, makes the structure of the displacement of the fore-and-aft direction that can absorb lever pin 6d.

In addition, in the substantial middle portion of feedback link 24, the said link pin 34 of pivot suspension, the point of action of formation link mechanism.

Promptly; Constituting is configured to make the fulcrum of feedback link 24 and the center of rotation of input side swash plate 6 to isolate to greatest extent; And the pivot connection (force) of feedback link 24 and input side swash plate 6 and the center of rotation of input side swash plate 6 are isolated to greatest extent; And then, the fulcrum of feedback link 24 and the pivot connection (link pin 34, point of action) of feedback link 24 and servo guiding valve 13 are isolated to greatest extent.At this moment, be formed on the roughly elongation line of each pivot point (that is, fulcrum, force, point of action each point) that connects feedback link 24 the center of rotation O of configuration input side swash plate 6 usually.

Thus, the amplitude in said force can be obtained to greatest extent, the resolving power of adjustment part 3b can be helped to improve.In addition, make point of action near doing one's utmost the force, also can obtain the amplitude of point of action significantly, can help to improve the resolving power of adjustment part 3b through formation.

Promptly; So that the center of rotation of the fulcrum of feedback link 24 and input side swash plate 6 is isolated to greatest extent; And the feedback link 24 and the pivot connection of input side swash plate 6 and the center of rotation of input side swash plate 6 are isolated to greatest extent; And then; The mode that fulcrum and the feedback link 24 that makes feedback link 24 and the pivot connection of servo guiding valve 13 isolate is to greatest extent made the structure of the pivot connection that disposed feedback link 24 and input side swash plate 6 and the pivot connection of feedback link 24 and servo guiding valve 13, thus, can improve the resolving power of hydraulic servomechanism 3.

Through constituting in this wise, be transformed into link pin 34 to the angle of the input side swash plate 6 that rotates by power piston 15 in the displacement of lower direction haply, corresponding therewith, feedback pilot valve 14 is slided on above-below direction.

That is, shown in figure 22, in the present embodiment, when being formed in input side swash plate 6 and clockwise rotating, feedback pilot valve 14 moves to upper position, and is shown in figure 23 in addition, when input side swash plate 6 rotates counterclockwise, and feedback pilot valve 14 displacement downwards.

In addition, through feedback pilot valve 14 displacements, it is flexible to constitute spring members 20, and the counter-force that by spring members 20 produced corresponding with it changes.Formation acts on servo guiding valve 13 by the counter-force that this spring members 20 produces, and servo guiding valve 13 is static on the position of counter-force that this spring members 20 of balance produces and the hydraulic pressure in grease chamber, said top 39.That is, make that in the neutral position slip of servo guiding valve 13 stops.

At this moment; Spring constant through suitably selected spring members 20; When hydraulic pressure and counter-force balance, the upper-lower position one that becomes servo guiding valve 13 is shaped as the state of said the 3rd form (that is, shown in figure 24, grease chamber, top 40 and grease chamber, bottom 44 and other disconnected forms such as grease chamber); The position that keeps power piston 15 constitutes feedback mechanism.

That is, constitute hydraulic servomechanism 3 and power piston 15 almost parallel ground configuration feedback link 24, make an end and input side swash plate 6 pivotal connections of feedback link 24 simultaneously; Make middle part and servo guiding valve 13 pivotal connections; The other end pivot suspension on input side housing 4, thus owing to can by power piston 15 input side swash plate 6 be toppled over accurately with simple structure; And with feedback link 24 servo guiding valve 13 is slided accurately, so can constitute high-precision feedback mechanism.

In addition, be formed in power piston 15 displacement rearward in the present embodiment, when input side swash plate 6 clockwise rotated in Figure 22, the rotation of outlet side swash plate 12 output increased; On the contrary, in power piston 15 displacement forwards, when input side swash plate 6 rotated counterclockwise in Figure 23, the rotation of outlet side swash plate 12 output reduced.

Owing to make outlet side swash plate 6 big from butt power that input side plunger 8 receives when deceleration side is rotated, so in order to make outlet side swash plate 6 in the bigger driving force of speedup side rotation needs in the butt force rate that outlet side swash plate 6 is received from input side plunger 8 when the speedup side is rotated.Therefore, power piston 15 rearward slides when speedup, that is, the situation of grease chamber, front side 17 pressurizeds of the big side of compression area through constituting power piston 15 in the speedup side can be made the structure of the same size that makes necessary driving force.

Thus, piston footpath, the hydraulic pressure supply pressure of power piston 15 are diminished.

Promptly; Be formed in power piston 15 when the direction of elongation is slided; In the mode of speedup side action input side swash plate 6 is rotated with Hyaulic infinite variable speed mechanism 1; And when the direction of shrinking is slided, in the mode of deceleration side action input side swash plate 6 is rotated with Hyaulic infinite variable speed mechanism 1 at power piston 15.Thus; Because in order to make 6 rotations of input side swash plate need bigger driving force in the speedup side; So when making the big face pressurized of compression area at power piston 15 (, when grease chamber, front side 17 side pressurizeds, power piston 15 slide to the direction of elongation); The structure that input side swash plate 6 is rotated in the speedup side can make the piston footpath and supply with hydraulic pressure to diminish.

More than to one embodiment of the invention, the explanation of the angular adjustment action of the input side swash plate 6 that is undertaken by hydraulic servomechanism 3.

The possibility of utilizing on the industry

The present invention not only can be used for various vehicles such as Motor Vehicle, agricultural operating vehicle, can also be widely used in purposes such as industrial machine.

Claims (5)

1. hydraulic pressure installation, it makes the oil hydraulic pump of plunger type variable capacity type or the movable swash plate of hydraulic electric motor fascinated by hydraulic servomechanism, it is characterized in that,

Said hydraulic servomechanism comprises: be connected with movable swash plate one end and fascinate fascinating of driving with piston,

Relatively this glide direction with piston of fascinating meet at right angles direction and the servo guiding valve that disposes with said movable swash plate almost parallel,

Connect this servo guiding valve and said movable swash plate feedback link and

Be provided with this servo guiding valve simultaneously and fascinate with the shell of piston with this,

Fascinate with the said feedback link of piston almost parallel ground configuration with said, simultaneously,

Make an end and the said movable swash plate pivotal connection of this feedback link, make middle part and said servo guiding valve pivotal connection, with the other end pivot suspension on said shell.

2. hydraulic pressure installation as claimed in claim 1; It is characterized in that; Make the said the other end of the said feedback link of pivot suspension on said shell as the fulcrum of this feedback link; So that the mode that the fulcrum of said feedback link is isolated from the center of rotation of said movable swash plate is to greatest extent set the position of this other end of this feedback link with respect to the pivotal bearing part of this shell; And the pivot connection of a said end and said movable swash plate that makes said feedback link is as the force of this feedback link; The mode of isolating to greatest extent from the center of rotation of said movable swash plate with the force of this feedback link; Set the position of this end of this feedback link, and then the pivot connection of said middle part and said servo guiding valve that makes said feedback link is as the point of action of this pivot connection with respect to the pivot connection of this movable swash plate; So that the mode that the point of action of this feedback link is isolated from the fulcrum of this feedback link is to greatest extent set this middle part of said feedback link and the position of the pivot connection of this servo guiding valve.

3. hydraulic pressure installation as claimed in claim 1; It is characterized in that; Said hydraulic pressure installation comprises the plunger and the cylinder body of accommodating this plunger with said movable swash plate butt; The low low pressure range of pushing force that this movable swash plate has the high high pressure range of the pushing force that receives from the plunger of butt and receives from the plunger of butt; Make said fascinating with the center of rotation of the said cylinder body of piston break-through, compare with rectangular of the center of rotation of said movable swash plate to the said high pressure range biasing of said movable swash plate be configured.

4. hydraulic pressure installation as claimed in claim 1 is characterized in that, said fascinating is made up of the cylinder bar with piston.

5. hydraulic pressure installation as claimed in claim 1; It is characterized in that; In the said occasion of fascinating and sliding to prolonging direction with piston; Said hydraulic pressure installation rotates said movable swash plate with the mode to the action of speedup side, and in the said occasion of fascinating and sliding to shrinkage direction with piston, said hydraulic pressure installation rotates said movable swash plate with the mode to the deceleration side action.

Images