CN101004194B - Compensation type drive especially for motor vehicle clutch - Google Patents

Abstract

An effort compensating actuator, especially for vehicle clutch, comprises an electromoter (10) used for driving a driving member (14) to move in a reciprocating course. Said reciprocating course comprises the following two sections: one section is used for adjusting compensating effort on a cam (24) and applied by springs (32, 34), wherein said cam is connected to the driving member; and the other section is used for moving a driven member of the clutch, during the separation and connection course.

Description

Be used in particular for the compensation type drive of automobile clutch

Technical field

The present invention relates to compensation type drive, it is used in particular for automobile clutch.

Background technique

For example by the known driver of file FR-A-2790806, in described driver, one force compensating spring be installed on one fixedly site and move converting member (moyen detransformation de mouvement) for example between a handle or the connecting rod, act on the active member of described driver, described active member drives a drive element of clutch, clutch release bearing (but é e d ' embrayage) for example, described clutch release bearing causes opening with closed of described clutch a predetermined reciprocating stroke mobile.Described counterbalance spring applies an active force to described active member, described active force is tending towards causing opening of described clutch, described spring can also reduce the steering force of described clutch, described steering force is provided by the power unit of an any kind, described power unit for example be hydraulic pressure or electric power.

For making the best performance of described driver, hope is exerted oneself quite by steering force and opening with closed of described clutch that described power unit provides.But the wearing and tearing of the friction facing of clutch disk show as described drive element be on the engagement positio move and described clutch is opened and closed change of exerting oneself, and these increase with wearing and tearing.

The variation of the steering force of described clutch can be regulated by the prestressing force of described counterbalance spring and be able to the small part compensation, and this can finish by the length of regulating described spring when described driver is in rest position.Described spring for example is installed on one fixedly between site and the bearing, described bearing can move with respect to described fixedly site by one bolt-nut system, and described bolt-nut system is being driven by the active member of described driver when the predetermined part of its stroke moves when described active member.

Consider that in prior art these force compensating adjustment stroke are arranged in a part and another part that described clutch open and close drives stroke, and the driving stroke of one of described two adjustment stroke and described clutch there is coincidence.Therefore, for example put---closed state of its corresponding described clutch---from a rest position of described driver, the one first force compensating adjustment stroke along the power augment direction is arranged, and after connect one and separate stroke, connect one stroke behind the described separation stroke itself, the trip is one to separate overtravel (sur-course) and and reduce the force compensating adjustment stroke of direction along power simultaneously.

But, the coincidence of the driving stroke of described clutch and an equilibrant force adjustment stroke has caused many problems.In fact, be difficult to realize driving overtravel and the dispersion (dispersion) of described equilibrant force adjustment stroke and the compromise between the amplitude of described clutch, this is especially because the driving stroke of described clutch bears many variations easily in time.

Summary of the invention

A kind of simple gratifying solution that the objective of the invention is to propose described problem is promptly: at the single part upper edge power augment direction of the active member stroke of described driver with reduce direction along power and regulate described equilibrant force.

The present invention proposes a compensation type drive for this reason, and it is used for one and is guided an especially for example automobile clutch of system, and described driver comprises: an active member, described active member are driven by a power unit on a reciprocating stroke; Spring force compensating parts, described spring force compensating parts link to each other with described active member by mobile converting member; Regulate parts with force compensating, described force compensating is regulated parts and is installed between at least one spring of described active member and described force compensating parts, and move by increment along an adjusting direction and an opposite direction, it is characterized in that, the reciprocating stroke of described active member comprises a first portion, described first portion extend that a rest position is put and one first moving position between, and on described force compensating adjusting parts, apply effect at the above active member of described first portion, and do not act on the described system that is guided, the described first portion of described active member stroke comprises one first section and one second section, described first section extends between a described rest position and the neutral position, and on described first section, described adjusting parts are driven by one first Compensation Regulation direction by described active member, described second section extends between another neutral position and described first moving position, and the above is regulated parts and is pressed another Compensation Regulation direction drive by described active member in described second section, the swing connected element is installed between described active member and the described adjusting parts, so that regulate towards a direction or other direction through the position in the aforementioned neutral position of its stroke first portion or another location according to described active member.

By parts should special combination, described force compensating is regulated with uncorrelated by the driving of the system of driver guiding, and does not influence described force compensating by may changing of the stroke of the drive element of the system of described driver guiding and regulate.

Described active member leaves a described drive element that is guided system at its rest position, and be resisted against on the described drive element in its second place, so that move described drive element by the remaining part that presses against its stroke, described drive element is actuated toward its initial position by elastic reseting part.

Described mobile converting member---it is installed between described active member and the force compensating parts---advantageously comprises a cam, described cam is moved by described active member and comprises a first portion and a second portion, wherein said first portion forms a bearing, when being moved in the first portion of described active member at its stroke, rolling parts as roller wheel bearing as described on the bearing; And described second portion forms a slope, and when being moved on the remaining part of described active member at its stroke, described rolling parts rest on the described slope.

By this layout, described force compensating parts are not acting on described active member when described active member is moved in its stroke first portion, and only work when described active member moves the described drive element that is guided system.

According to another characteristic of the invention, described force compensating parts comprise two coaxial springs, and described two coaxial springs are installed in parallel, and have only wherein a spring can regulate parts by aforementioned force compensating on length and regulate.

Therefore, described force compensating is regulated with respect to a non-zero mean, and described force compensating regulates and require than regulating described two littler power of power that the length that is installed in parallel spring needs simultaneously, and described force compensating is regulated a unique spring that only relates in described two springs.

Of the present invention one preferred embodiment in, described force compensating is regulated parts and is comprised one bolt-nut system, according to the shift motion of described active member and direction, towards a direction or other direction drives rotationally or drive non-rotatingly, and the nut of described system forms a bearing of described force compensating adjustable spring to the bolt of described system by described active member.

The bolt of described bolt-nut system is being driven and is rotating by bistable position swing ratchet (cliquet basculant à deux portions stables) by described active member, wherein said ratchet by the supporting of described active member and and one with described bolted gear matched, when described active member was in its rest position or its second place, described ratchet ran to another settling position from a settling position.

Implement in the modification one, the bolt of described bolt-nut system is rotated by a gear driven by described active member, described gear is connected with bolt and cooperates with two teeth that drive rotation, described two teeth are formed on the described active member in the both sides of described gear, and they stagger on the movement direction of described active member mutually.

This breaks away from described gear on the track and can laterally move with respect to aforementioned driving gear in one; And it is directed in the very big V-way of an opening, thereby described gear is moving around its rotation by an aforementioned cingulum that is moved along an assigned direction by active member, and is pushed open on described disengaging track along the same tooth that moves in the other direction but not around its rotation.

According to another feature of the present invention, described gear the axle by a bearing for example ball bearing be directed in the described guide rail, described gear has a circle involute shaped ring gear (denture end é veloppante de cercle) and comprises 6 or 8 teeth, and aforementioned profile of tooth is formed on the two long limits of an opening of described active member, perhaps is formed on the two long limits of opening of a member that is moved by described active member.

According to another feature of the present invention, described profile of tooth is formed on the member, and described member is installed perpendicular to the axle of described active member shifting axle rotationally around one.

As modification, be formed with member translation on a straight path of aforementioned tooth on it, described straight path is parallel to the motion track of described active member.

Be formed with a same cam or the cam face of supporting of member of described tooth, rolling parts act on described cam or the cam face, and described rolling parts are subjected to described one or more force compensating spring actuated.

Usually, carrying out driving the risk that the described drive element that is guided system can make described driver standardization and reduce design inferior and bad operation on force compensating adjusting and described active member second stroke on described active member first stroke, wherein said second stroke is different from described first stroke and does not coincide with it.And, finish described force compensating adjusting and need not sensor and extra power unit.

Description of drawings

By with reference to description in conjunction with the accompanying drawings follow-up and that carry out with by way of example, the present invention will be able to better understanding, and further feature of the present invention, details and advantage be more than you know, and accompanying drawing comprises:

Fig. 1 is the schematic exploded perspective view of one first mode of execution of one driver according to the present invention;

Fig. 2 is the partial enlarged view of described driver front surface, and it shows the part that force compensating is regulated parts;

Fig. 3 regulates the perspective diagram of looking up of parts for described force compensating;

Fig. 4, Fig. 5 and Fig. 6 are the schematic representation of corresponding diagram 1, and it shows the running of described driver;

Fig. 7, Fig. 8 and Fig. 9 are that described force compensating is regulated along the schematic representation of the mode of execution of a direction and other direction;

Figure 10 and Figure 11 are line charts, and it shows described force compensating and regulates;

Figure 12 is the schematic exploded perspective view of second kind of mode of execution of driver according to the present invention;

Figure 13 is the local enlarged diagram that described force compensating is regulated parts, and it shows the power that puts on the gear;

Figure 14 is the less partial schematic diagram of another magnification ratio that described force compensating is regulated parts;

Figure 15 shows described force compensating and regulates the running of parts in described second kind of mode of execution.

Embodiment

The driver that the present invention provides---its first kind of mode of execution is by shown in Fig. 1 to 11---schematically shown in Figure 1, mainly comprise a motor 10, described motor mounting is on a casing 12, in order to move a cylindrical rod 14 in axial translation mode by a gear 16, wherein said gear 16 is driven by the output shaft of described motor 10, and meshes with a tooth bar 18 that carries described cylindrical rod 14 (cr é maillere).

Described cylindrical rod 14 and described tooth bar 18 are led in the translation mode in described casing 12, described bar 14 effects are to move a piston 20 by pushing in the translation mode, described piston shaft is in a cylinder that is slidingly mounted on a ram pot 22, moving of the release bearing (not shown) of described ram pot control automobile clutch is with the described clutch of open and close.

Described tooth bar 18 supports a ramp type cam 24 (came à rampe oblique), described cam upper support has the rolling parts, for example roller 26, described roller is rotatably installed on the transverse axis 28 that is had by a movable component 30, described movable component in described casing 12 along perpendicular to the shifting axle of described cylindrical rod 14 and described piston 20, be directed (Fig. 2) with vertical move mode.

Described movable component 30 has two supporting parts with shaft helical spring 32,34 bottoms of supporting, and described two spring diameters are different, and one of them is placed in another, and their top nestles up the groove bottom 36 of movable component in the described casing 12.

The spring 32 of described outside bears against fixedly on the shoulder of described movable component 30 in its bottom, and the spring 34 that is positioned at described spring 32 inside bears against on the nut 38 in its bottom, the position of described nut can be regulated by vertical translation in the groove at the seat of described spring 32 and 34, the power that applies with the length that changes described spring 34 and described spring.

Described nut 38 is screwed into the on the threaded vertical bar 40, and described bar extends axially in the inside of described spring 32 and 34, and its bottom is guided in the bearing that is installed on described movable component 30 bottoms and rotates.One protruding pin 44 convexes to form in the periphery sides of described nut 38, and it is entrenched in the guiding groove, it is not rotated and makes its axial translation with fixing described nut 38, and wherein said guiding groove is formed in the inner cylinder of described movable component 30.

The bottom of described threaded bar 40 is connected with a gear 46 (Fig. 3), and a described gear and a bistable position ratchet 48 cooperate, and described ratchet is installed rotationally around the pivotal axis 50 on the described movable component 30.

Described ratchet comprises two pawls 52 radially, the opening that described radially pawl passes a chute 54 extends, described chute supports described ratchet, and it can the translation mode move by described tooth bar 18 by means of a horizontal pawl 56, wherein said horizontal pawl 56 is entrenched in the opening of a plate 58, and described plate is fixed on the described cam 24 that is connected with described tooth bar 18.The opening of described plate 58 comprises a top, the pawl 56 of described chute embeds wherein, and this makes, when the cylindrical rod 14 of described driver is mobile in described driver stroke first portion, can drive described chute and described ratchet 48, more details will provide below.

The bottom of described opening is defined by hypotenuse 60 vertical edge relative with that is parallel to described cam one slope.

Described cam 24 comprises two levelling benches that link to each other by a slope 66, i.e. upper mounting plate 62 and lower bolster 64.

Described swing ratchet 48 comprises two teeth 68 on the one hand, described two teeth can with the tooth interlock mutually of described gear 46, described on the other hand ratchet comprises described two pawls 52 radially, described two radially pawl with each other at a distance of 60 ° angle orientation, and backstop is on the opposite edges 70 of a horizontal opening of described movable component 30, so that the swing of described ratchet in succession.A slice spring 72 is fixed on the described swing ratchet 48 by an end, and pivots around the pivotal axis on the described movable component in its other end, is in one of two settling position to keep described ratchet 48.

The running of described compensation type drive is illustrated to Fig. 6 by Fig. 4.

Among Fig. 4, described driver is positioned at its rest position, and the closure that is guided clutch shown in the correspondence of described position is a jointing state, and described cylindrical rod 14 is positioned at the back position (right side on the figure) of its stroke latter end and leaves the described piston 20 that the described clutch of control is opened.

In described position, the roller 26 of described movable component 30 abuts against on the upper mounting plate 62 of described cam 24, and described spring 32 and 34 the biggest ground pressurized.

Among Fig. 5, described cylindrical rod 14 has been moved towards the front by described motor 10, and just move in the left side on the figure, on the piston 20 of the described tube of opening near the described clutch of control.

In described position, the right roller 26 of described movable component 30 is positioned at the top on the slope 66 of described cam 24, described left wheel 26 lucky junction points on described upper mounting plate 62 and described slope 66, and the pawl 56 of described chute 54 has moved left by the top court of described plate 58 openings, and described plate is fixed on the described cam 24.One first portion of the mobile formation described driver stroke of described cylindrical rod 14 between rest position shown in Figure 4 and position shown in Figure 5, it does not influence the clutch of described driver guiding at all, and only be used to regulate described spring 32 and 34 and act on power on the described cam 24, described cam is connected with described tooth bar 18.

When described cylindrical rod 14 is moved just in time up to position shown in Figure 6 by described motor 10 towards the front, the position of opening fully of the corresponding described clutch in described position, described spring 32 and 34 loosen gradually up to described roller 26 be positioned at described cam 24 lower bolster 64 near, described left wheel 26 had been rolled on the almost whole length in the slope 66 of described cam.Described piston 20 has been moved towards the front by described motor 10 simultaneously, described motor drives described cylindrical rod 14 by described gear 16 and described tooth bar 18 by described spring 32 and 34 and moves towards the front, described spring applies an oblique active force by described left wheel 26 on described slope 66, the horizontal component of this oblique active force is offset described clutch force.

When described cylindrical rod 14 and described cam 24 moved between Fig. 5 and position shown in Figure 6 towards the front, the hypotenuse 60 of the opening of the plate 58 that the pawl 56 of described chute 54 supports along described cam 24 slided, and does not move towards the front.The second portion of described cylindrical rod 14 strokes---it allows to open described clutch fully---does not therefore influence the position, angle of described swing ratchet 48 at all.The hypotenuse 60 of described opening has been reduced to necessary bottom line with (d é battement) between the wheel shaft trip of described chute 54 and therefore can have reduced the volume of described driver.

Adjusting by described spring 32 and the 34 described equilibrant forces that provide is described to Figure 11 by Fig. 7 now.

Fig. 7 a shows the different relative position of described bar 14 described swing ratchet 48 and described gear 46 during moving back and forth on the entire first portion of described driver stroke to Fig. 7 g.

Among Fig. 7 a, described driver is positioned at its rest position (closed condition of described clutch), and described ratchet 48 is positioned at one of two settling position, and only to rotate by counterclockwise direction on figure, its reciprocal rotation is forbidden at the described ratchet in described position.

When described driver is controlled to move in the first portion at its stroke described bar 14, it is by the position shown in Fig. 7 b, this moment, one tooth of described ratchet 48 was engaged in the tooth of described gear 46, and this tooth of gear 46 illustrates to be different from other tooth of described gear with black.In follow-up position shown in Fig. 7 c, described ratchet 48 makes described gear 46 deasil rotate a tooth pitch and breaks away from from described gear.In the position shown in the subsequent figure 7d, a pawl 52 of described ratchet 48 bears against on the aforesaid one stroke latter end block 70, described ratchet thereby rotate widdershins and run to its another settling position.As shown in Figure 5, the latter end of the first portion of the corresponding described driver stroke in described position.

When described bar 14 when described driver rest position is moved in opposite direction, described ratchet 48 is brought to the position shown in Fig. 7 e from the position shown in Fig. 7 d, then arrive the position shown in Fig. 7 f, engage into a tooth of described gear 46 at the described ratchet in this position, and this position be positioned at the tooth shown in the described black near.Because described ratchet 48 can not be widdershins rotates around its axle in described position, thereby when the stroke latter end position that runs to from the position shown in Fig. 7 f shown in Fig. 7 g, this ratchet makes described gear 46 rotate a tooth pitch widdershins.Can see that described gear 46 has turned back to its position, angle that occupies in Fig. 7 a.

Fig. 8 illustrates the regulative mode that reduces the described equilibrant force of direction along power.Fig. 8 a is illustrated in the described ratchet 48 under the described driver rest position, this ratchet when Fig. 8 b illustrates described ratchet and meshes a tooth of described gear 46, and Fig. 8 c illustrate be in as the back position as described in ratchet: in this position, ratchet is after making described gear deasil rotate a tooth pitch, it breaks away from from described gear, and described position is the same with the position shown in Fig. 7 c.

Be returned to its rest position if follow described driver, 48 on described ratchet is got back to the position shown in Fig. 8 d, and it meshes described gear 46 again described position.At this moment, described ratchet is arranged in the settling position identical with Fig. 8 c with Fig. 8 a, Fig. 8 b, and it can rotate a tooth pitch widdershins, and can not deasil rotate.Therefore, when described ratchet by described driver when its rest position is taken back, make the widdershins rotation of described ratchet shown in Fig. 8 e with contacting of described gear 46, and described gear 46 rotated.Shown in Fig. 8 f and Fig. 8 g, when its rest position shown in Fig. 8 g of described driver vicinity, a pawl 52 of described ratchet is run into a block 70, thus described ratchet conversion settling position.

Described equilibrant force is illustrated to 9g by Fig. 9 a along the regulative mode of power augment direction.

Position shown in Fig. 9 a, described ratchet 48 is positioned at the right of described gear 46, the position shown in this corresponding diagram 7e, described driver thereby be positioned at position shown in Figure 5.In described position, described ratchet 48 is in a settling position, and on the described position, it is only deasil to rotate.When described driver was brought back to its rest position, described ratchet 48 was moved towards the left side shown in Figure 9 and shown in Fig. 9 b and 9c, makes described gear 46 rotate a tooth pitch widdershins.

The stroke of described driver was blocked before described rest position, and described driver is replied and not conversion settling position towards its initial position direction shown in Fig. 9 e.As a result, shown in Fig. 9 d and Fig. 9 e, when it meshed described gear 46 once more, it did not drive described gear 46 around it pivots, then when it arrives the first portion end of described driver stroke, and promptly shown in Fig. 9 g during the position, the conversion settling position.

Described driver moves back and forth so shows as described gear 46 and rotates a tooth pitch in the counterclockwise direction on the part area of the first portion of its stroke, the increase of equilibrant force described in the embodiment that this correspondence provides.

The adjusting of described force compensating is illustrated by Figure 10 and Figure 11 equally, and they illustrate stroke variation of t in time between position D (separated state, clutch is opened) and position E (jointing state, clutch cuts out) of described driver.

Among Figure 10, described driver rotates a tooth pitch at mobile closure and the described gear 46 that shows as described clutch on the first stroke C1 between position D and the position E in the direction that described equilibrant force increases, and this this portion C 1 relevant symbol+1 by described curve illustrates.If following described driver is moved and was stopped in neutral position P2 before arriving this separation initial position P1 towards its direction of separating initial position P1, this shows as described gear 46 and rotates a tooth pitch in opposite direction, and the symbol-1 that the portion C 2 of curve is relevant is represented as described.

Described driver then as described shown in the portion C 3 of curve, is returned to its rest position, and described gear 46 is rotated.In follow-up lock out operation, as described shown in the portion C 4 of curve, its whole stroke between described driver described position E of process and the D, and cause that when current described gear 46 rotates along the direction that described equilibrant force reduces, this is represented as the relevant symbol-1 of this curved portion C4.Described separation is therefore to finish than in the past little equilibrant force.

Figure 11 illustrates the adjusting of described equilibrant force along the direction of its increase.For this reason, after the separation, described driver is replied towards its rest position E direction on C ' 1, but symbol+1 that before arriving described rest position and as described curved portion C ' 1 is relevant is shown in the direction that described gear 46 is increased along described equilibrant force rotate after, be blocked in neutral position P3.Then shown in C ' 2, described driver is returned to and separates initial position P1, gets back to its rest position E then shown in the 3rd curved portion C ' 3.Therefore it makes described gear 46 rotate along the direction that described equilibrant force increases once more, and symbol+1 is represented as described.

Shown in curved portion C ' 4, when follow-up lock out operation, the direction that described driver makes described gear 46 reduce along described equilibrant force is rotated a tooth pitch, as described shown in symbol+1.But generally, described equilibrant force increases a tooth pitch (pas).

To sum up, in the time should reducing described equilibrant force one tooth pitch, between described position E, P2 and E, move back and forth described driver; And in the time should increasing described equilibrant force one tooth pitch,, move back and forth described driver then between the P1 at described position P1, P3 then.

When the change of the described equilibrant force of direction that increases when the direction that reduces at described equilibrant force or described equilibrant force must be very big, these that repeat repeatedly described driver on demand were reciprocal.

Each tooth pitch that described gear 46 rotates along a direction or other direction shows as moving that the rotation of described screwed bar 40 and described nut 38 face upward or downward, described nut forms the bearing of described spring 34, and therefore also shows as the described length change that is positioned at the spring of rest position.This can make described equilibrant force center on a mean variation to compensate the wearing and tearing of described clutch, and described wearing and tearing show as the increase of described Separating force.

In the mode of execution shown in Figure 12 to 14, the motor 10 of described driver drives a tooth bar 18 by one speed reducer and described gear 16, described gear is installed on the output shaft of described motor, be fixed with the cylindrical rod 14 of described driver on the described tooth bar, as the mode of execution of front, described bar moves the piston 20 of the hydraulic control tube 22 of a clutch release bearing.

Described cylindrical rod 14 comprises two side arms 80, and the end of described side arm embeds in the perforate 82 of arm 84 of a balace weight (balancier), and the arm 84 of described balace weight is installed pivotally around a fixedly transverse axis 86 that is positioned at described arm top.

Described arm 84 bendings are L-shaped and partly lean on the transverse slat 88 of a basic horizontal to be connected to each other therebetween, and described plate 88 is positioned at the top of described tube 22 and belongs to described driver equilibrant force regulates parts.

The force compensating parts of described driver preferably include two coaxial springs 90, described spring is installed between a securing supports and the movable component, described movable component has the support roller 92 that is supported on the cam face, and described cam face is formed by the part of the basic horizontal of described equalizer arm 84.The power that described spring 90 puts on the described equalizer arm is tending towards making described arm to rotate around described transverse axis 86 widdershins, and applies a thrust at the described detaching direction in described cylindrical rod 14 upper edges.

On the contrary, during clutch, the described bar 14 that is driven by the described motor 10 of driver deasil rotates described arm 84 around described transverse axis 86 just.

The mode of execution that described equilibrant force is regulated parts such as front comprises: a nut 94, described nut forms the bearing of one or two spring, described nut is screwed into the on the axial stem and is being driven by a gear 96 and rotates, described gear is installed on the end of a vertical cylindrical rod 98 regularly, and described bar itself is driven by another gear 100, described gear 100 vertically embeds in the opening of described transverse slat 88, and it is driven along a direction or other direction by two teeth 102 and 104, and described two teeth convex to form on two of the opening of described plate 88 relative longitudinal edges.

The width of described opening is greater than the external diameter of described gear 100, described gear 100 can laterally move in described opening, and the bottom 106 of the axle of described gear is guided in the very big V-arrangement cross slide way 108 of an opening, described guide rail is expressed as a guide shaft fixing unit 110, its described transverse plate 88 and control described clutch release bearing the tube 22 between.

One unshowned Returnning spring is in to being positioned at described plate 88 open interior that the gear 100 of position applies active force in the middle of it constantly.

Described gear 100 has a circle involute profile of tooth circle and comprises 6 to 8 teeth.

The equilibrant force adjusting that drives described gear 100 by described tooth 102 is illustrated with schematic form by Figure 15.

In the phase I of described adjusting, shown in Figure 15 a, a toe joint of described tooth 102 and described gear 100 touches, and the tooth of described gear illustrates to be different from other tooth with black.

When described tooth 102 as Figure 15 a in the 15f shown in the arrow by when move the front, it makes described gear 100 deasil rotate a tooth pitch as shown in the figure, and described gear 100 does not break away from from described guide rail 108, and reason is that the opening of described V-way is rearward-facing and gear 102 is moved forward.

When described tooth 102 as Figure 15 g when being returned to its initial position shown in the arrow among the 15l, it promotes the tooth of described gear 100, described gear thereby can break away from from described guide rail 108, and therefore leave described tooth 102 and not around its rotation.

When described tooth 102 was got back to its initial position shown in Figure 15 l, with respect to the position shown in Figure 15 a, described gear 100 had deasil rotated a tooth pitch, and increases described equilibrant force by the length that reduces one or more of counterbalance springs.

In the time should reducing described equilibrant force, described just tooth 104 drives described gear 100 forward widdershins when its quilt is mobile, and described just tooth 104 cause described gear 100 laterally moving in described guide rail 108, and described gear does not rotate around its axle in its return stroke backwards.

For remaining, described running is similar with described first kind of mode of execution: described motor 10 moves described cylindrical rod 14 forward to be separated to form, described forward mobile is subjected to the auxiliary of described counterbalance spring 90, described spring applies a couple on described equalizer arm 84, described couple is tending towards making described arm to rotate widdershins, as shown in figure 12.

Described equilibrant force is performed such along the adjusting of a direction or another direction: be resisted against on the piston 20 of described application cylinder 22 at described bar 14 and before beginning to move described piston 20 in described tube, described bar 14 is reciprocal back and forth in the first portion of its stroke forward.Two teeth 102 of described plate 88 and 104 relative in the vertical staggering, before the described tooth of regulating along the equilibrant force augment direction 102 is positioned at and reduces tooth 104 that direction regulates along described power, so that described adjusting along the equilibrant force augment direction is finished in the first portion of the stroke of the described bar 14 that begins from described driver rest position, and finish on the next part of the stroke of the described bar 14 that begins from described rest position, and begin to move at described bar 14 before the piston 20 of tube 22 of the described clutch release bearing of control along the adjusting that described power reduces direction.

The end 106 of the axle of advantageously described gear 100 is furnished with a bearing, and for example a ball bearing does not roll so that it has on the wall of described guide rail 108 frictionally, and the end of the axle of wherein said gear is accepted in the described guide rail 108.

Equally advantageously, the round involute shaped ring gear of described gear 100 is specified to: in the position shown in Figure 15 f or the 15g---and drive the end of rotating and the beginning of described disengaging described in the corresponding described guide rail 108 in described position, described gear 100 is orientated symmetrically with respect to a transverse axis perpendicular to the movement direction of described driving gear 102.

These comment the gear 46 that is suitable for described first kind of mode of execution equally.

Usually, the present invention is applicable to the clutch of all kinds, tension or pushed away, normally open or normally close, described driver and described clutch be connected can be hydraulic pressure or machinery.

Claims (18)

1. compensation type drive, it is used for one and is guided system, and described driver comprises: an active member (14), described active member are driven by a power unit (10) on a reciprocating stroke; Spring force compensating parts, described spring force compensating parts link to each other with described active member by mobile converting member (24,26); Regulate parts (38,46) with force compensating, described force compensating is regulated parts and is installed between at least one spring (34) of described active member and described force compensating parts, and regulates direction and along one and move by increment in the opposite direction with this adjusting side,

It is characterized in that, the stroke of described active member (14) comprises a first portion, described first portion extend that a rest position is put and one first moving position between, and on described force compensating adjusting parts, apply effect at the above active member of described first portion, and do not act on the described system that is guided, the described first portion of described active member stroke comprises one first section and one second section, described first section extends between described rest position (E) and one first neutral position (P2), and on described first section, described force compensating is regulated parts and is driven by one first Compensation Regulation direction by described active member, described second section extends between one second neutral position (P3) and described first moving position (P1), and the above is regulated parts and is pressed another Compensation Regulation direction drive by described active member in described second section, swing connected element (100) is installed between described active member and the described adjusting parts, so that according to described active member through aforementioned neutral position (P2, P3) one first neutral position in or second neutral position and regulate towards a direction or other direction.

2. according to the described driver of claim 1, it is characterized in that, described active member leaves a described drive element (20) that is guided system at its rest position, and be resisted against on the described drive element at its first moving position (P1), so that move described drive element by the remaining part that presses against its stroke, described drive element (20) is actuated toward its initial position by elastic reseting part.

3. according to claim 1 or 2 described drivers, it is characterized in that, described mobile converting member comprises a cam (24), described cam is moved by described active member (14) and comprises a first portion (62) and a second portion, the first portion of wherein said cam (62) forms a bearing, when being moved in the first portion of described active member at its stroke, rolling parts (26) are bearing on the described bearing; And the second portion of described cam forms a slope (66), and when being moved on the remaining part of described active member at its stroke, described rolling parts (26) rest on the described slope.

4. according to the described driver of claim 1, it is characterized in that described force compensating parts comprise two coaxial springs (32,34), described two coaxial springs are installed in parallel, and have only wherein a spring can regulate parts (38 by aforementioned force compensating on length, 46,48) regulate.

5. according to the described driver of claim 4, it is characterized in that described two springs (32,34) diameter is different, and their inside that is arranged in another.

6. according to the described driver of claim 1, it is characterized in that, described force compensating is regulated parts and is comprised one bolt-nut system, the bolt of described bolt-nut system (40) is being driven step by step by bistable position swing ratchet (48) by described active member (14) and is rotating, wherein said ratchet (48) is moved by described active member and cooperates with described bolted gear (46) with one, when described active member is in its rest position or aforementioned neutral position (P2, one of P3) time, described ratchet (48) runs to another settling position from a settling position.

7. according to the described driver of claim 6, it is characterized in that described ratchet (48) is moved in the translation mode by described active member (14).

8. according to the described driver of claim 6, it is characterized in that, the bolt that described force compensating is regulated the bolt-nut system of parts is driven rotation by described active member by a gear (100), described gear and two drives the driving gear (102 that rotates, 104) cooperate, described two driving gears are on the both sides of described gear (100) are formed at a member with described active member associated, and described two driving gears stagger on the movement direction of described active member mutually.

9. according to the described driver of claim 8, it is characterized in that described gear (100) breaks away from the track and can laterally move with respect to aforementioned driving gear (102,104) one; And, the axle of described gear (106) is directed in a V-way (108), described guide rail is orientated to: described gear (100) is by an aforementioned driving gear (102 that is moved along an assigned direction, 104) axle that drives around described gear rotates, and pushed open on described disengaging track along the same driving gear (102,104) that moves in the other direction but do not rotated around the axle of described gear.

10. according to the described driver of claim 9, it is characterized in that the axle (106) of described gear (100) is directed in described guide rail (108) by a bearing.

11., it is characterized in that described gear (100) has a circle involute shaped ring gear according to claim 8 or 9 described drivers.

12., it is characterized in that described gear (100) comprises 6 or 8 teeth according to the described driver of claim 8.

13., it is characterized in that the described driving gear (102,104) that drives described gear rotation is formed on two longitudinal edges of an opening according to the described driver of claim 8, described opening is formed in the member, and described member is moved by described active member (14).

14., it is characterized in that the described driving gear (102,104) that drives described gear rotation is formed on the plate (88) according to the described driver of claim 8, described plate centers on an installation rotationally perpendicular to the shifting axle of described active member (14).

15. according to the described driver of claim 14, it is characterized in that, hold the driving gear (102 that rotates with described driving, 104) described plate (88) belongs to the part of a balace weight (84), described balace weight comprises cam face, rolling member (92) acts on the described cam face, and the stressed counterbalance spring of described rolling member (90) is actuated.

16., it is characterized in that the described system that is guided is an automobile clutch according to the described driver of claim 1.

17., it is characterized in that described rolling parts (26) are rollers according to the described driver of claim 3.

18., it is characterized in that described bearing is a ball bearing according to the described driver of claim 10.

Images