CN1120133A - Friction clutch - Google Patents

Abstract

The present invention provides a friction clutch for use with a clutch disc, particularly for motor vehicles, the clutch having a pivot support for a diaphragm spring which acts on an axially displaceable pressure plate in the direction of the clutch disc and of a counterpressure plate.

Description

Friction clutch

The present invention relates to a kind of friction clutch that is used in particular for Motor Vehicle, has a platen, its antitorque ground but can limited vertically mobile being connected with housing, simultaneously, axially the dish spring is pushed in one of tensioning between housing and platen, it can rotate around a pivoting support by the housing supporting on the one hand, can execute towards the direction of a clutch disk platen on the other hand and carry, this clutch disk can clamp between above-mentioned platen and opposed pressing plate such as flywheel, wherein be equipped with a controlling device, it is used to compensate the wearing and tearing of the friction pad of clutch disk.

Automatic control tegulatingdevice, it should press the dish spring to stable power load of platen effect by agent, for example discloses in DE-OS2916755 and 3518781.Simultaneously, this controlling device that can regulate according to a sensor at least is placed in or acts between platen and the extruding dish spring.Because the platen on the operation housing is the blade spring by tangential arrangement, so its power can only be quite little, because the extruding force of this power and dish spring is a reverse direction, like this, when friction clutch separates, this platen with quite big quality just may be swung vertically, also can leave simultaneously from the dish spring, thus, performance of clutch not only is affected, and clutch even the safety that can become are critical, and this is because controlling device is to regulate under the state that disconnects, all like this before platen rests on clutch disk, clutch just can not separate again like this.For this reason, the controlling device of this form is actually obsolete.

Task of the present invention is, eliminates above-mentioned defective and the controlling device of the above-mentioned type is improved, so that it can be applied in the broad practice and under rough working order.It has the performance of simple structure and safety durable, needs a less construction space and cheap for manufacturing cost in addition.Also have, essential Separating force can be less, and all keeps less in whole length of life, and in addition, the operating life of friction clutch also is enhanced.

The present invention of this task so solves, promptly can execute in the friction clutch that carries pressing platen with the dish spring, wherein, a dish spring produces extruding force, this dish spring is bearing on the member as housing on the one hand, and the opposing party can be around a pivoting support swing, and this pivoting support is arranged on the housing with round structure, acting on an automatic controlling device between housing (housing) and dish spring, it depends on the supporting abrasion of case side and the displacement of leaving from housing; This controlling device can be caused continuing to move by a work feeder, and this dish spring is in one under the supporting force effect of pivoting support direction.According to the purpose requirement, this supporting force is permanent the existence, and therefore, this dish spring is only supporting on the contrary and by a spring force with power closed manners and Separating force, rather than support by the hinged device of rigidity.Simultaneously, the dish spring is provided with to such an extent that have decrescence a characteristic line in its operating range, and, supporting force and disc spring force are so to determine mutually, promptly, supporting force the dish spring rigging position of regulation change with not relevant tapering with wearing and tearing and the dish spring separate in the stroke time be greater than apply by the dish spring with supporting force opposite effect power, and the dish spring have with the relevant tapering situation of change of wearing and tearing under, supporting force in the part separation stroke zone of dish spring be less than apply by the dish spring with supporting force opposite effect power.Supporting force can be by an independent spring element or is produced by an independent spring element or spring element system at least basically simultaneously.Still be interpreted as the spring force summation (as long as they can find) of all and dish spring adverse effect about " supporting force ", for example even or only by the power of blade spring effect (transmission of torque-or lifting-), and (residue-) elastic force of pad spring, or its " deposit ".

As the power storage, it applies supporting force at least basically, can require to use a spring according to purpose, and it changes its structure by adjusting, for example, is a dish spring.This applies the power storage of supporting force, also can constitute by the blade spring.

A dish spring that applies supporting force can be directly installed on the dish spring, for example is installed on the radial height of axially movable case side supporting tongue.

Particularly advantageous mode is to be placed between dish spring and the clamshell on controlling device is axial.This controlling device can contain rise surface such as sloping platform by the mode that meets purpose especially.

Can guarantee by the present invention, the dish spring can be considered during the operating life of friction clutch, in fact when friction clutch engages, always have identical tapering or tension force and one and be applied to active force actual constant on the platen and therefore, the wearing and tearing that guarantee clutch disk and these members are irrelevant, as friction pad, platen itself or other elements (the supporting tongue of clamshell or platen side, the friction surface of dish spring or flywheel).Can guarantee also by standard of the present invention that in addition the quality of platen can not increase owing to the quality of controlling device yet.In addition, this controlling device is positioned in such zone, promptly can protect it to avoid the influence that mill decreases and try one's best away from frictional heat source in this zone.

Particularly advantageous organization plan of friction clutch of the present invention is, this extruding dish spring is to be bearing on the housing pivotally between two parts, wherein, execute towards extruding dish spring with spring mode facing to the part of platen and to carry, simultaneously, act on spring when the clutch separation by extruding dish spring and execute the active force that carries on the supporting member and under pad part abrasion condition, increase, and become and prop up reaction force or supporting force on the part greater than acting on spring-loaded.Simultaneously, extruding dish spring has a characteristic line like this, that is, and and based on the rigging position of its structure qualification in friction clutch, on lax (unloading) direction that causes because friction pad weares and teares, this is increased at least by power and the essential thus Separating force that extruding dish spring applies; And continue at the rigging position that limits relatively on the position of distortion or tensioning, this can be reduced in separation process by the power that extruding dish spring applies.So structure and configuration are just guaranteed by extruding dish spring, occurring under the pad part abrasion condition, always can when separating, be applied to the power on the part again and act on spring and execute between the reaction force that carries on the part and be adjusted to a balance by extruding dish spring, because, surpass under the supporting force situation in the power that is applied to by this dish spring on the part, this dish spring just makes sensing spring move away from a part of housing side, and thus, controlling device just can further be rotated by the active force of work feeder.Like this, part just moves axially, until the power that applies by sensor can prevent controlling device be rotated further and stop prop up a part and continue to move axially till.

Particularly advantageous mode is, as carrying, will push the dish spring and so be placed in the friction clutch, promptly pushes the dish spring at least in a part of separated region, preferably in fact has the force characteristic curve of a decline in whole friction clutch separated regions.The rigging position that pushes the dish spring simultaneously can be that under the friction clutch separated state, in fact extruding dish spring reaches or surmounted the minimum value or the low valley point of its sinusoidal power-stroke curve.

Execute the reaction force that applies on year part at spring, can produce by a power storage by optimal way, it can apply a constant power at least in the regulation range of regulation.Particularly advantageous mode be a corresponding construction setting and in friction clutch to give the dish spring of tensioning state assembling.

Controlling device of the present invention can particularly advantageous mode be applied in the friction clutch, wherein, have an extruding dish spring, it is executed platen with the zone that is positioned at the outside on radially and carries, and by the area supporting between two revolution parts that is provided with inwards continuously on housing.In this structural type, this dish spring can be used as the caliper lever and works.

But the present invention is not confined on the friction clutch with the dish spring (it is the separator levers of dish languid that this dish spring has structure).The present invention can also be extended on other the clutch configuration, and at this moment, for example, this dish spring is by additional lever.

The time regulate without doubt and the friction clutch extruding force an of the best in order to ensure wearing and tearing, particularly advantageous mode can be, extruding dish spring (with spring execute carry a part away from) opposed part being provided with on the side be structure like this setting, promptly, this opposed part vertically can be automatically or moving of can't help towards the direction of platen, but just can be braked automatically or in spite of oneself in the opposite direction, by a device.And the adjusting of opposed part that is clamshell side can be finished by a power storage, and it applies effect to this opposed part towards the direction of platen or facing to extruding dish spring.Like this, automatically regulate, according to this, just can guarantee to push gapless pivoting support of dish spring and can make opposed part fill up the displacement that part wearing and tearing cause admittedly according to spring-loaded part.

This opposed part can move axially by a controlling device that is provided with between extruding dish spring and cap.Simultaneously this controlling device can have an annular that is member that self link up, and it is extruded the dish spring at the jointing state of friction clutch at least and executes vertically and carry.When wearing and tearing occurring and during separation process, rotate the member of above-mentioned annular, pivoting support is carried out and the consistent adjusting of pad part wearing and tearing.For this reason, particularly advantageous mode is the adjusting sloping platform that the annular construction member of this controlling device or this controlling device has rising vertically.In addition, presumable advantage is, this annular member is equipped with opposed part, and simultaneously, the available one metal wire ring of this opposed part constitutes.This wire rings can be contained in one of above-mentioned annular construction member around annular groove in, and be being connected of coincideing of structure with this member.This structure is coincide and can be arranged to sting card connection simultaneously.

This rising (adjusting) sloping platform can be married again the body mating reaction with the cylindrical or class of regulating usefulness is spheroidal.But particularly advantageous is that therefore rising sloping platform and corresponding opposed rising sloping platform collaborative work, just can realize that one self is braked by the angle of climb of suitably selecting these sloping platforms under the axial tensioning situation of sloping platform.Opposed rising sloping platform can place on the annular construction member, and it can be placed between rising sloping platform and the housing.But a simple especially structure realizes by opposed rising sloping platform is set on housing.This opposed rising sloping platform can be made on plate shape housing with simple especially mode.Because this opposed rising sloping platform can be realized in punching out.Simultaneously, this punching out member can be arranged in the zone of radially extending on the housing.

For guaranteeing to make inexpensively friction clutch, favourable in addition mode can be that at least a portion controlling device is made of plastics.And this class plastic member can be made with injection moulding.As plastics, advantageous particularly and suitable be for example polyamide of thermoplastic materials.Because controlling device is to be in the zone of seldom bearing heat effect, is possible so use plastics.In addition, because less weight also can produce a very little moment of inertia.

According to other design of the present invention, this controlling device is the structure setting so, and promptly it is seen on the friction clutch detaching direction, the effect of similar zero load, but this moment, and the direction opposite with detaching direction is braking itself.For this reason, rising sloping platform and/or the so structure setting of opposed rising sloping platform, they have an angle of climb in the axial direction, and this angle is preferably in the order of magnitude of 5 to 12 degree between 4 and 20 degree.Favourable mode is that rising sloping platform and/or the structure setting like this of opposed rising sloping platform promptly produce one by rubbing contact and self brake.But this self braking can also realize or strengthen by a respective outer side edges, and wherein, for example sloping platform is soft then to equip corresponding profile with another sloping platform, and perhaps wherein two sloping platforms all have profile.Just guarantee by this measure, needn't just can avoid undesirable resetting with additional device.

The advantageous particularly of this controlling device and simple proposal may be, the spring that will become give tight installation at the work feeder of circumferencial direction effect, it is equipped with the member of rising sloping platform and/or member that is equipped with opposed rising sloping platform or opposed elevated areas to one of major general and applies elastic load towards the direction of controlling device.Simultaneously, spring-loaded can so realize by advantageous manner, i.e. the performance of other springs executes that the spring performance of carrying should not be subjected to or in fact unaffected as special operation dish spring with to a part of axial elasticity.

For some application, favourable mode can be that controlling device has a plurality of movably regulating elements, for example radially and/or along the circumferential direction movably regulates wedge or rolling element.Favourable in addition mode can be that controlling device is relevant with revolution.Like this, for example under just can considering as the working state of determining at internal-combustion engine, operates and/or the kayser controlling device centrifugal force that acts on the discrete component of controlling device.Particularly can brake this controlling device from certain revolution of determining by the device that depends on centrifugal force, this point for example can be at least near unloaded revolution or be lower than on the revolution of this unloaded revolution and realize, in order that wear adjustment is only carried out under less revolution.Such advantage is, undesirable adjusting can not occur, because under the vibration situation of undesirable adjusting may occur in high revolution the time.

A controlling device organization plan simple especially and reliable performance can so guarantee, that is, these relative housings movably and the member with rising sloping platform and/or opposed rising sloping platform or opposed elevated areas by spring-loading.As long as also exist one to have the relatively member that moves of housing of corresponding sloping platform or zone, this member just should be executed year so.Particularly advantageous mode can be simultaneously, and this elasticity is executed and carried the active force that produces a circumferencial direction.

In addition, structure and performance for friction clutch can advantageous mode be, this sensor spring of being arranged to disc spring such as dish spring on the member as housing of an axial restraint, and applies power load with the zone of radially continuing to be provided with inwards to propping up a part away from the revolution (rolling) of housing with its area supporting that is positioned at the outside on radially.This revolution (rolling) part can also be arranged to holistic structure with this sensor spring, in order that this sensor dish spring also constitutes supporting member.For the sensor spring is fixed on the tension position, can also make housing be equipped with support region.These support regions can constitute by the independent supporting element of installing on housing.But favourable mode can be, support region is and the holistic structure of housing, for example, pressing product or otch and zone distortion can be set on housing, and they block in the bottom with axially mounting and live this sensor spring.

Work operation for friction clutch, particularly be in order to reduce Separating force or to reduce the essential particularly advantageous mode of maximum separation power, the clutch disk that can clamp between platen and opposed pressing plate has friction pad spare, a so-called pad spring is set between them, for example disclosed such in DE-OS3631863.By using the clutch device of this form, be very favourable to the operation of friction clutch, particularly separation process.This be because, under the jointing state of friction clutch, clamped pad spring applies a reaction force on platen, it is with extruding dish spring or to operate the active force that the dish spring acts on the platen just in time opposite.In separation process, and during the moving axially of platen, this platen is at first returned by the pad spring of elastic tension and is squeezed, simultaneously, because the steep relatively drooping characteristic line that extruding dish spring exists at separated region, so the power that is applied on the platen by this extruding dish spring descends.The power that acts on the platen along with extruding dish spring descends, and the returning place force that is applied on this platen by the pad spring also descends.This effectively separates the necessary active force of friction clutch is to be produced by the returning place force of pad spring and the extruding force difference of extruding dish spring.After the pad spring is lax, that is at platen when friction pad leaves or friction clutch when discharging by platen, this essential Separating force is mainly by the decision of extruding dish spring.Power-the stroke characteristic of the power-stroke characteristic of pad spring and extruding dish spring can determine that promptly when friction clutch discharged by platen, the necessary active force of operation extruding dish spring was on the low level so mutually by favourable mode.That is can by on purpose make pad spring performance and extruding dish spring characteristic before releasing clutch consistent or even balance each other, just can only need one very little, under extreme case even actual unwanted, the steering force that is used to push the dish spring is finished remaining (separations) driving.In addition, the characteristic of extruding dish spring can so be provided with, after clutch disk discharges, this apply by extruding dish spring with the opposite opposed power of revolution in other words for making extruding dish spring turn round necessary power, with respect to being in for the extruding force that the friction clutch jointing state applies on the very low level by pushing the dish spring.Can also so be provided with, at this moment, under by platen releasing clutch dish situation, only need a very little or actual no power, just can operate extruding dish spring and come cut-off clutch.Such friction clutch can so dispose, and promptly steering force places in 0 to 200N the order of magnitude.

According to additional design of the present invention, this friction clutch can so be provided with, promptly, at least pass through under the platen release conditions at clutch disk, by approximate being in the null range of axial force that extruding dish spring applies, simultaneously, proceeding under the separation process situation, the power that is applied by extruding dish spring can be negative value, that is the power effect of extruding dish spring turns to.This means that separate fully under the situation at friction clutch, in fact this clutch keeps self opening state, and has only the power effect by the outside, this clutch's jointing process just can import again carries out.

The present invention relates to a kind of friction clutch in addition, be specially adapted to Motor Vehicle, has a platen, its antitorque ground but axially can limited mobile being connected with housing, simultaneously, an effectively extrusion spring of tensioning is set between housing and platen at least, and along the direction imposed load towards a clutch disk, this clutch disk can clamp between platen and opposed platen (as flywheel) with platen for it.

Such clutch for example at DE-OS2460963, disclosed among the DE-PS2441141 and 898531 and among the DE-AS1267916.

Task of the present invention in addition is, the performance and the operating life of the friction clutch of this form are improved, particularly by the present invention, operating the necessary active force of this class friction clutch can reduce, and guarantees in fact to have during operating life a stable Separating force curve.In addition, friction clutch of the present invention can also simple and economical especially mode be made.

The present invention of this task so realizes, promptly be provided with a controlling device to the wear automatic-compensation of friction clutch friction pad, it is by the Shi Zaili of extruding dish spring to a practical stability of platen effect, and friction clutch has operation equipment and device that is used for clutch, this device is in separation process, at least separate stroke at a part of operational stroke of operation equipment and/or in the part of platen, cause little by little reducing by friction clutch or clutch disk torque transmitted.Device by this type can realize equally, under beginning jam between platen and the opposed platen, little by little or progressively increased by the friction clutch torque transmitted in the engaging process of friction clutch with at friction pad.

Configuration by friction clutch of the present invention is just guaranteed, during the operating life of friction clutch, in fact extruding dish spring always has identical tension under friction clutch joint situation, therefore, can realize that platen is had an in fact stable power load.In addition, can realize that by the device that replenishes Separating force or essential maximum separation power reduce or reduces to minimum.This point depends on that this device helps the operation of friction clutch, particularly separation process.For this reason, this device can have the device of axial elasticity distortion, and it is applying a reaction force on operation equipment and/or on the extrusion spring and/or on the platen and/or on the opposed platen, and it acts on the power reverse direction on the platen with extrusion spring and is connected in series wherein.

Particularly advantageous mode can be, this device of friction clutch can so be settled, during separation process, this device causes torque little by little to reduce in by the axially displaced stroke of a part in the platen scope of extrusion spring imposed load, and this torque is transmitted by friction clutch or clutch disk.

For some application, this device can be arranged on the pivoting support of operation equipment by favourable power transfer mode and between the housing fixed position such as bolt on the opposed platen, perhaps is arranged on extrusion spring and between the housing fixed position (as bolt) on the opposed platen.

But the mode favourable for other applicable cases can also be, this device is arranged in the power transmission between the friction surface of the pivoting support of operation equipment and platen or between extrusion spring and the platen friction surface.This configuration structure has for example been proposed in DE-OS3742354 and DE-OS1450201.

For other applications, can particularly advantageous mode be, this assembly axis upwards be arranged between two clutch disk friction pads of settling back-to-back, that is, constitute with one so-called " pad spring ", for example constitute by the pad spring sector that between the pad part, is provided with.The device of this form is for example open in DE-OS3631863.

Another program is to realize that a progressive torque increases or reduces, this is known in DE-OS2164297, and wherein, flywheel is made two members, and the member that constitutes opposed platen is that the relative members shaft that is connected with the live axle of internal-combustion engine is to flexibly mounted.

May meet the mode that purpose requires especially for the performance of friction clutch of the present invention and structure is, this device can realize between the clutch member one axially on flexible flexibility, simultaneously, this device is so settled and structural arrangements, promptly under clutch separates situation, the power that acts on this device is minimum, and, in the closing course of clutch, that is in the clutch stroke, the power on this device of acting on be rise to gradually peaked, simultaneously, this raising according to the purpose requirement, only occurs in a part of closing stroke operation equipment or platen or the joint stroke.Can particularly advantageously be that the so configuration of this device is in promptly above-mentioned approximate at least 40% to 70% scope that reduces or increase gradually the operational stroke that occurs in operation equipment and/or platen maximum axial stroke gradually by the friction clutch torque transmitted.And all the other zones of corresponding stroke, for separating the power transmission without doubt and being equilibrated on the friction clutch particularly clutch disk, the distortion that may exist on platen and the opposed platen is essential.

For making the required power of operation friction clutch of the present invention reduce to minimum, may particularly advantageously be, this extrusion spring, at least separate in the stroke at a part of friction clutch and have a power-stroke curve that successively decreases, that is mean, this extrusion spring has the force curve of a decline at least in the part (zone) of its compression stroke or deformation stroke.Just can realize thus, in the separation process of friction clutch, the power adverse effect of the spring force of this device and extrusion spring, like this, in a part of zone of separating stroke, the tension of extrusion spring or distortion just obtain the support of the elastic force of this device, simultaneously, because extrusion spring exists at separated region and passs power-stroke curve gradually or that descend, then be applied on the platen or the power of friction pad spare reduces by extrusion spring.In order effectively to separate the necessary power change curve of friction clutch, under not additional and spring action stack, be that the difference between the power change curve of the power change curve that applied by this device and extrusion spring produces.When platen left under the friction pad situation or by platen clutch disk discharged, the Separating force change curve that must leave over or essential Separating force were mainly determined by extrusion spring.Power-the stroke curve of this device and the power-stroke curve of extrusion spring can be so definite mutually, promptly pass through under the platen release conditions at clutch disk, for the required power of operation extrusion spring is on the low relatively level.That is spring performance that can be by making this device or force characteristic until clutch is close with the characteristic of extrusion spring before discharging or even balance each other, then only need a very little active force of in fact (even not using) the operation extrusion spring at extreme case.

As extrusion spring, Shi Yi advantageous manner is a dish spring especially, and it can turn round around an annular pivoting support by the housing supporting on the one hand, again platen is applied power load on the other hand.Simultaneously, this dish spring has a ring body, is provided with the footpath thus and yearns for the interior tongue spare that points to and extend, and they constitute operation equipment.But this operation equipment also can constitute by lever, and it for example is placed on the housing pivotally.Yet, the extruding force that is used for platen can also be by other form of springs, for example helical spring produces, these springs are so to be placed in the friction clutch, promptly, the axial force that is applied on the platen by these springs is to be in peakedly at the friction clutch jointing state, and this power is gradually little during separation process.This point for example can be by realizing the spin axis tiltably-mounted of the relative friction clutch of helical spring.

May particularly advantageous mode be that the dish spring is bearing between two parts on the housing, so that constitute the clutch of a so-called compression structure form pivotally.Under this clutch situation, the operation equipment general fashion that is used to separate friction clutch is that the direction towards platen is loaded.But the present invention not only is confined to the clutch of compression structure form, but also comprises the clutch of stretched out structure form, wherein, is used to separate that the operation equipment general fashion of friction clutch is loaded towards the direction of leaving platen.

The particularly advantageous mode of friction clutch of the present invention can have a dish spring, it is arranged to have a sine-shaped power-stroke curve and so assembling, promptly at the state of friction clutch joint, its operation point is set in place the characteristic line zone decrescence after the first power maximum value.Simultaneously, can particularly advantageous mode be that it is 1: 0.4 to 1: 0.7 force rate value that the dish spring has a value between the first power maximum value and power minimum value thereafter.

In addition, may be particularly advantageous be that friction clutch can be by a clutch system operation that for example connects at the lip of the tongue of dish spring on operation equipment, simultaneously, this clutch system can have a clutch pedal, the structure of its similar gas pedal and being placed in the Motor Vehicle inner room.The clutch pedal of this kinds of structures can be particularly advantageous, because, be provided with by structure of the present invention, can be arranged on the very low level in order to separate necessary power of friction clutch or power change curve, like this, just can realize a steering force control preferably by the clutch pedal of a similar gas pedal structure.

By the friction clutch of structure of the present invention and the possibility of the maximum extrusion spring power of the life period appearance that can be reduced in friction clutch that links to each other therewith, member is correspondingly diminished or component strength is reduced, thus, just can make manufacturing obviously cheap.In addition, by reducing Separating force, also make in the clutch and piece-rate system in loss and elastic loss reduces and according to this, make the efficient of this system friction clutch/clutch system that important improvement be arranged.Therefore, whole system can be provided with and then make the operating characteristics of clutch obviously to improve best.

Organization plan of the present invention generally can be applicable in the friction clutch, is specially adapted in these clutches, for example by DE-PS2916755, DE-PS2920932, DE-OS3518781, DE-OS4092382, FR-OS2605692, FR-OS2606477, FR-OS2599444, FR-OS2599446, GB-PS1567019, US-PS4924991, US-PS4191285, US-PS4057131, JP-GM3-25026, JP-GM3-123, JP-GM2-124326, JP-GM1-163218, JP-OS51-126452, JP-GM3-19131, the clutch that JP-GM3-53628 proposes.

In addition, the invention still further relates to old application DE-P4207528.9, its content obviously belongs to disclosure of the present invention.

Use a kind of at least can be automatically or the friction clutch that compensates in spite of oneself to pad part wearing and tearing, owing to can guarantee at least clutch disk to be applied an approximate constant clamping force at the workpiece life period of friction clutch, so, it is particularly advantageous being connected application with clutch pack, wherein, friction clutch, clutch disk and opposed platen (for example flywheel) constitute an assembly unit or a module.In the assembly unit of this form, the mode favourable for cost be, clutch housing and opposed platen be connected to non-disconnectable connection set, for example, be welded to connect, or moulding connects, for example the material deformation by plasticity.By the connection of this form, the general fixing device of using as bolt, just can be saved.Under this assembly unit situation, owing to having surpassed wear mark and change clutch disk or clutch pad spare, do not destroy member (as clutch housing) and be practically impossible.But by using the clutch of compensate for wear, this assembly unit can so dispose, that is, a unquestionable performance can be guaranteed in this unit during whole Motor Vehicle operating life.That is, structure is provided with according to the present invention, the adjusting deposit of the wearing and tearing deposit of clutch disk and friction clutch or clutch module can be made so greatly so that life of clutch and according to this operating life of assembly unit can reach corresponding life-span of Motor Vehicle at least reliably.

According to flexible program of the present invention, can particularly advantageously be, friction clutch and so-called two mass block flywheels with wear compensation device are combined, simultaneously, this friction clutch can settle a clutch to be assemblied on the flywheel mass piece that can link to each other with gearbox by the centre.And the second flywheel mass piece can be connected with the live axle of internal-combustion engine.Wherein can use two mass block flywheels of friction clutch of the present invention, for example at DE-OS3721712, DE-OS3721711, known in 4117582 and 4117579.The full content of these applications also belongs to disclosure of the present invention, and therefore, the feature of describing in these applications can be combined with the feature of the present invention's record in any manner.Especially, clutch housing or clutch housing can not destroy with regard to non-disconnectable connection set by one and be connected with the flywheel mass piece that is loaded with this clutch, as in each embodiment of DE-OS4117579 the expression and as described in.

By using a friction clutch of the device of band compensation pad part wearing and tearing at least, just can realize the setting of a friction clutch optimization in addition, but particularly the subtend clutch disk applies the power storage realization optimization setting of tension force.That is this power storage is provided with, and its only actually will transmit the torque necessary clamping force of wishing and put on the clutch disk.This power storage can constitute with at least one dish spring or a multi-circle spiral flow spring.In addition, it is favourable using that a friction clutch of self regulating combines with the mass block flywheel, wherein, be arranged on (radially) outside of clutch disk or be arranged on outside (radially) of outside friction diameter of the flywheel piece friction surface that can be connected at the rotation elastic damper that two flywheel interblocks are settled with gearbox.Under this two mass block flywheel situations, the friction diameter of clutch disk is affirmed the friction diameter less than the conventional clutch dish, in order that squeezing action power must improve according to the relation of mean friction radius, so that can transmit the engine torque of a qualification.Using under traditional clutch situation, can cause the raising of clutching force like this.But, but the clutch of the compensate for wear by using the record of claim 1 (promptly, a kind of friction clutch that is particularly suitable for Motor Vehicle, has a platen, this platen is not rotating but can do axially that limited mobile mode links to each other with shell, a dish spring that produces extruding force is axially compacted between shell and platen simultaneously, this dish spring is on the one hand around the pivoting support revolution that is bearing on the shell, on the other hand platen is pressed to a direction between platen and the opposed platen as the clutch disk that clamps of flying wheel, one of them can compensate and be carried continuously by an advancing means the wearing and tearing of the friction pad of clutch disk at least, and act on that the pivoting support that is being supported by shell in the automatic control tegulatingdevice can move in the axial direction between housing and the dish spring, and the dish spring is in the direction towards pivoting support under the effect of support force.) because it has a characteristic that little by little reduces by the clutch disk torque transmitted in separating stroke, so, just realize that a Separating force descends, therefore just can avoid the raising of Separating force.Perhaps can realize fully that by corresponding configuration friction clutch the Separating force of a relative conventional clutch descends.

Like this, can guarantee that though the friction pad outer diameter reduces and essential thus higher extruding force, Separating force still can remain on low level by the structure setting of a friction clutch of the present invention.Because lower Separating force also makes the load of (two flywheel mass pieces are relatively turnable at it) rolling bearing reduce.In addition, by the wear adjustment device, the life-span of clutch has improved, and therefore, changes member, and it is just unessential particularly to change clutch disk during the Motor Vehicle operating life.Also have, the clutch clamshell can be fixedly connected with the flywheel mass piece that can be connected gearbox, for example by riveted joint or welding.Yet this is particularly advantageous, because have the clutch housing of a qualification or the profile of qualification, and this profile can not allow by bolt the clutch clamshell to be connected with the flywheel of gear-box side in a conventional manner this moment.

Under the friction clutch situation that the controlling device that will be used to fill up the part wearing and tearing is integrated in one, when the clutch unit of being made up of friction clutch and flywheel is fixed to an internal combustion engine drive axle in a conventional manner, axial, vibration that rotate and that wave just is delivered on the clutch unit, and this vibration is the live axle by internal-combustion engine, and particularly crankshaft causes.For the performance that makes clutch unit or controlling device be unlikely because of this vibration influenced, particularly make wear compensation device can suppress a undesirable adjusting, when the configuration adjustment device, just must consider the inertial force of the member that those work so on this device.For fear of these undesirable side effects that causes because of axial and unstable vibration especially, in other words for avoiding the relevant therewith expense that is used for the configuration adjustment device because of the wearing and tearing of compensation pad part to improve, according to another design of the present invention, this clutch unit with controlling device loses with the axial and flexure vibrations that caused by the internal combustion engine drive spindle guide as far as possible synchronously.This point can realize so that promptly clutch unit can be connected with the live axle of internal-combustion engine by a member axial elasticity or camber of spring.The rigidity of this member is so to determine simultaneously, promptly by the live axle of internal-combustion engine on clutch unit, produce axially and wave and flexure vibrations, damped at least or be suppressed to one quantitatively by this flexible member, at this moment, can guarantee friction clutch, particularly its controlling device has unquestionable performance.This flexible member, for example in EP-OS0385752 and 0464997 and SAE TechnicalPaper900391 known.Equally, the content of these open files belongs to content disclosed by the invention.Just can will cause special when friction clutch separates, vibrate by flywheel and/or the wear adjustment of not wishing that the vibration of dish spring causes eliminates by platen with respect to the axial vibration of clutch clamshell by using a resilient member.The vibration of this form, in the friction clutch assembly or clutch unit of the device that does not have to suppress at least basically this vibration (dish of the special as axial deformation of this device), then can cause an adjusting with the irrelevant variation of the state of wear of clutch disk, simultaneously, the dish spring extruding force of friction clutch may be turned down towards a power minimum value, therefore no longer guarantees to transmit the torque of hope.

According to another organization plan of the present invention, one has automatically or the friction clutch of the compensation device of can't help,-this compensation device can be especially carries out among the driving car of structure setting-can be applied in an advantageous manner according to the present invention, particularly in the driver element of Motor Vehicle, and this driver element is made up of driving the friction clutch of settling between motor (as an internal-combustion engine) and the gearbox and control or regulate operation at least according to the action of gearbox an automatic or automanual gearbox and one.This friction clutch preferably can be operated fully automatically.Automatically or fully automatically operate, for example propose by DE-OS4011850.9 for one of friction clutch.Like this, please refer to these documents about working method and essential device.

At existing band automatically or in the driver element of semiautomatic gearbox and traditional friction clutch, the obvious problem that exists be the operation of clutch and operate essential actuator (as piston/cylinder unit and/motor) configuration.Owing to high relatively Separating force essential in conventional clutch, so need actuator very strong or big specification.This just means big structural volume, high weight and high cost.The actuator that also has this big specification is owing to its mass inertia, so the time for acceleration is just slow.This external application is regulated under cylinder situation, and the just essential bigger volume flowrate of pressure unit like this, is supplied with pump size and also must be strengthened relatively, so that guarantee operating time that is applicable to corresponding friction clutch of wishing.In order partly to eliminate aforementioned shortcoming, for example propose at DE-OS3309427, to reduce to be used for the steering force of cut-off clutch, just can use the actuator of small dimension size by the corresponding compensation spring according to this.Because, Separating force in traditional clutch is during operating life but strong swing, that is to say, Separating force is less relatively when new state, but rise in the work increase along with the pad wearing and tearing in service, so, can only reduce a part essential Separating force usually by a counterbalance spring.Considering under total manufacturing tolerances situation, although adopt counterbalance spring, still essential actuator separative power, and it is greater than the power of a new conventional clutch.By the friction clutch that adopts the present invention to have fill up wear compensation and one by motor and the driver element automatic or semiautomatic gearbox is formed, the relative prior art of Separating force is reduced fairly obviously, and directly show in the clutch, simultaneously, in fact new clutch separation power value or Separating force curve remain unchanged in its whole operating life.Just produce the significant advantage that is suitable for actuator arrangement thus, because its driving power or operand power just can remain on the corresponding low level, simultaneously, power that occurs in entire separation system or pressure are also corresponding less.According to this, the loss that occurs owing to the friction or the elasticity of member in piece-rate system is eliminated or reduces to a minimum value.

In addition, the present invention relates to a kind of friction clutch, be specially adapted to Motor Vehicle, has a platen, it is antitorque, but axially can limited mobile being connected with housing, simultaneously, an operation equipment and power storage are set between housing and platen at least, by this power storage, this platen can be by the direction imposed load towards a clutch disk, and this clutch disk can clamp between platen and opposed platen (as a flywheel), wherein, a controlling device that wearing and tearing compensate to the friction pad of clutch disk at least is set.

This part wearing and tearing can be regulated according to pad self regulates clutch, and are for example known in DE-PS2920932 and DE-OS3518781.

In this clutch, but wear adjustment is to realize by the supporting member of an axial adjustment between platen and dish spring, simultaneously, this part is bearing on the platen by sloping platform, with be implemented in the adjusting on the dish spring direction or wedge wherein correspondingly be set by rotation along the circumferential direction, their mating reactions between the plane of inclination of platen or part platen.

For knowing the situation of pad wearing and tearing, in two embodiments, a plurality of sensor elements that work between platen and flywheel or clutch cover are set, it can be regulated according to the pad wearing and tearing under the closed situation of clutch, and under the clutch separation situation, the clutch (stroke) of platen is limited on the definite value.

Simultaneously, because under the new state of clutch, the dish spring shifts out and the identical stroke that separates of platen in the scope of supporting when cut-off clutch.If fill up when wearing and tearing, then platen is towards the direction displacement of flywheel.Under this state of wear, the dish spring will than platen more in the scope of supporting and move the stroke equal wear extent, therefore, supporting just can be on the direction of dish spring according to the gap adjustment of generation.

The adjusting of this form may be that work is insecure in practice, because the clutch motion itself of dish spring is to be dispersed in quite consumingly in the dish languid portion in constant clutch stroke situation, and the very big separation stroke of generation scatters on this external separation support.So just cause, when regulating clutch system, for example under the mechanical type clutch system, may make a mistake, for example between segregating unit and dish spring, transfer to the load of giving of a too small excesssive gap.Will make clutch produce diverse operating point thus.

Using the piece-rate system of self regulating, for example having transmission and accepting in the hydraulic system of cylinder, this system may be out-of-operation at all, because, during operating life, as long as the clutch campaign of dish spring is less than or equal to the words of platen motion in support region, then on the clutch gross output looks with the separation stroke, and then just can not regulate, if the dish spring is carried out a detaching motion bigger than platen on the contrary with above-mentioned, then in each lock out operation, take place irrespectively to regulate, this clutch is just regulated after the time of weak point and reached an end so with the pad wearing and tearing.

There is another problem in the existing clutch of self regulating, and platen can be excited into self resonance (vibration), and leaves the dish spring vertically simultaneously, can cause the complete controlled clutch of controlling device like this.

For this reason, the other task of the present invention is, the friction clutch of a type noted earlier is set, and has an improved controlling device of relative prior art.Simultaneously this controlling device is simple in structure and take the small construction space.In addition, this friction clutch can also be made in simple and cheap especially mode.

The present invention of this task so realizes, promptly between operation equipment and platen that joint and separation for friction clutch are provided with, a wear compensation device is set, it passes through the power storage in fact constant power load of platen effect, wherein, it carries out an axial positioning corresponding with the state of wear of friction pad by a controlling device corresponding with wearing and tearing between operation equipment or power storage and platen, simultaneously, reaching under the situation of the adjusting corresponding with the actual wear state of friction pad, this wear compensation device is limited or blocks its adjusting function by the device that is provided with on platen.According to the present invention a device is set on platen like this, it can prevent that the adjusting of compensation device from exceeding the wearing and tearing stroke of actual generation, simultaneously, and the adjusting of wearing and tearing and the qualification of this adjusting all carried out in the separation process of clutch.

Performance and structure for friction clutch, may particularly advantageously be, the dish spring of an axial tensioning is set between housing and platen, it can turn round around a ring-shaped bearing by the housing carrying, and it has a matrix annular and that constitute the power storage, radially extends into tongue inward to form operation equipment by matrix.

The qualification measure of this compensation device can constitute by at least one wear sensor by plain mode, it has movably sensor component of a relative platen at least, and this sensor component is by limiting the separation stroke of platen on the member that rests on an axial restraint.The member of this axial restraint can be made of clutch housing or opposed pressing plate simultaneously.As favourable mode, this sensor component can so be constructed and be placed on the platen, that is, during the operating life of friction clutch, make the relative housing of platen keep the separation stroke of a practical stability.

For guaranteeing that wearing and tearing have a unquestionable compensation to pad.May particularly advantageous mode be that the relative platen of this sensor component is a retainer shaft to movably.To this, this sensor component not only can be indirectly by one automatically or the controlling device of can't help or but also can directly be connected with housing, and do and fill up corresponding the moving of wearing and tearing by on the member that rests at least one axial restraint and relative platen.This moves, and requires to take place during clutch's jointing process according to purpose.What be used for sensor component can be arranged on the clutch housing and/or opposed platen by putting the zone.By wear sensor being rested on the member of corresponding axial restraint, this compensation device just can be unloaded during separation process, therefore, exist under the pad abrasion condition, compensation device just can be regulated, till this mating reaction of regulating regulating element by this compensation device and sensor component is defined.

May favourable mode be that a plurality of wear sensors that distribute on the circumference of platen are set, they can guarantee the location that the rotating shaft at the relative friction clutch of dish has a nothing to beat in the separated state of friction clutch.

May favourable mode be, sensor component has one by putting the zone, and it is relative to putting regional mating reaction with compensation device compensation member or regulating element one when friction clutch separates.Guarantee that platen has the sensor component of a constant separation (stroke) controlling device automatic by in an advantageous manner or that can't help to be connected with platen.A kind of like this controlling device can be by the closed connection set formation of friction between sensor component and platen, simultaneously, in clutch's jointing process, surpass under the deterministic force situation, this friction closure just is overcome, thus, the relative platen of sensor component carries out and the corresponding adjusting of actual wear that descends.But, this controlling device also can realize by the device of a similar idle running, it is in clutch's jointing process, allow the relative platen of sensor component to carry out an adjusting, under the friction clutch separation case, this sensor component then is blocked by the relative platen of controlling device in contrast.

One is used to compensate the controlling device of filling up wearing and tearing organization plan simple especially and reliable operation in friction clutch inside and can so guarantees, promptly this compensation device comprises that is used for the power storage support member of a dish spring (as be in particular), and a compensation device is set between support member and platen, it causes support member to carry out an automatic wear adjustment under the friction clutch separation case, and self brakes when clutch.This means that when support member unloaded, this compensation device was released, and when support member loaded, this compensation device kept its adjusted position, that is be lockable.To this maybe advantageously, this support member can be axially moves along the direction of tripping dish, and towards platen axially on can be braked.This compensation device can act on with as dallying under the friction clutch separation case simultaneously, but self brakes when clutch.

Simple especially organization plan of compensation device can be realized to form a compensation member by using an annular construction member.This annular member can be by the sloping platform supporting in the face of platen simultaneously.These sloping platforms can with opposed sloping platform mating reaction, simultaneously, this press advantageous manner can mutually tensioning by at least one spring element.And sloping platform and opposed sloping platform can constitute by the member of single member such as wedge shape, and they can be placed between the member of platen and annular.But at least one sloping platform group can directly made on the annular construction member or on the platen.Therefore, a friction clutch simple in structure just can so be realized, promptly, this annular member be arranged to take the shape of the letter U hollow sheeting structural member of cross section, simultaneously, in the free chamber of this member, be equipped with distribute along circle with the tapered member that forms sloping platform, and the member of these wedge shapes can be by advantageous manner and annular antitorque connection of member.A favourable compensation device organization plan can also so finish, promptly the member of this wedge shape relatively the member of annular be removable leading in the axial direction.Same opposed sloping platform can be made by the member of wedge shape, and it embeds in the free chamber that is surrounded by the compensation member of annular at least in part vertically, and can rotate relative to platen and compensation member.Thus, additional advantage can be that the relative platen of this compensation device is to keep antitorque.For guaranteeing automatic regulating action of compensation device, this opposed sloping platform can be spring-loading on the direction of sloping platform.This spring-loaded can be by the spring of tensioning between the member that forms sloping platform and opposed sloping platform, and for example helical spring is realized, simultaneously, they can be contained in the annular free chamber neutralization of compensation member equally and be arranged to pressure spring with advantageous manner.And the member that constitutes opposed sloping platform is contained between the compensation member of the member that forms sloping platform and annular at least axial component.For guaranteeing that the spring of sloping platform and opposed sloping platform tensioning is fixed and leading with carrying out no problem, can be advantageously, the end regions of this spring at least, leading by the member that constitutes sloping platform and opposed sloping platform.For this reason, this corresponding member can have addition or projection, and they extend to the end regions that gives tension spring at least.Simultaneously, these springs can always be arranged between two tapered members, and tapered member is to do antitorquely with this annular support member, but movably connect axially, and another tapered member is adjacent and support member is rotating relatively at circumferencial direction.

The member that constitutes sloping platform and/or opposed sloping platform can be made of plastics with simple mode, for example by an injection moulding process.As plastics, advantageous manner is to use for example thermoplastic of heat-insulating or heat-resisting plastics, or thermosetting plastics (Duroplaste).Simultaneously maybe advantageously, the material that constitutes sloping platform member and/or opposed sloping platform member has a high friction factor (value), and it is positioned at the order of magnitude of the friction valve of friction pad material.Bearing angle by suitably selecting sloping platform and/or opposed sloping platform and suitably be chosen in sloping platform and opposed sloping platform between friction factor compensation device can so be set, promptly under axial tensioning situation, can finish self braking.For this reason, the structure setting like this of sloping platform and/or opposed sloping platform, they have an angle of climb in the axial direction, and it is preferably in 5 ° to 12 ° the order of magnitude between 4 ° and 20 °.Like this, just can guarantee by compensation device correspondingly is set that this compensation device is self braking at the friction clutch zygophase, therefore, the device that does not need to add just can avoid compensation device that undesirable return takes place.

Make so tensioning of power storage of sloping platform and opposed sloping platform tensioning, promptly when taking place or have the wearing and tearing of pad part, always carry out an adjusting, and this wear adjustment can also occur under the clutch situation of rotation.Simultaneously,, can so realize that the i.e. performance of remaining spring is not to be subjected to or in fact impregnable as particularly operating dish spring and the blade spring that platen is connected with housing or housing with advantageous manner to the spring-loaded of sloping platform and opposed sloping platform.

But for some application, favourable mode also may be that this controlling device depends on revolution.Like this, for example can operation and/or this controlling device of locking under the certain running state of internal-combustion engine will be used at the centrifugal force that acts on each element of controlling device.Particularly, the device that this controlling device can be by depending on centrifugal force is lockable when certain revolution or when surpassing a definite range of revolution.For many applicable cases, can also be advantageously, this controlling device so is provided with, and promptly it only works being similar under the idle revolutions at least or being lower than under the situation of idle revolutions, and like this, wear adjustment only may be carried out under less engine speed.The device that makes wear adjustment device realization locking or unclamp can be made the member of this compensation device by favourable mode, for example makes by the member that forms sloping platform and/or opposed sloping platform.

For the adjusting function of compensation device, may particularly advantageous mode be when clutch separation, to be greater than leaving (stroke) to the dish spring stroke on the diameter region of platen imposed load by the gauge device or by the definite platen of wear sensor at the dish spring.Just can guarantee according to this, rest on the member of an axial restraint at the gauge device after, this compensation device is unloaded and then no longer regulate.

According to another inventive features scheme, this compensation device can have two sloping platform structures by putting mutually, simultaneously, a sloping platform structure is antitorque with respect to platen, and another sloping platform structure is antitorque with respect to the compensation member by power storage imposed load, wherein, this compensation member is rotating with respect to platen.

In addition, the invention still further relates to a kind of friction clutch that is specially adapted to Motor Vehicle, has a platen, its antitorque ground also axially can limited mobile being connected with housing, simultaneously, axially the dish spring is pushed in one of tensioning between housing and platen, it can be turned round by the annular pivoting support of housing supporting around one on the one hand, on the other hand to the direction imposed load of platen towards a clutch disk that between this platen and opposed platen (as a flywheel), clamps, simultaneously, a controlling device that the wearing and tearing of the friction pad of clutch disk are compensated is set, it is by the power load of extruding dish spring to a practical stability of platen effect, wherein, between extruding dish spring and platen, wear compensation device is set, it has an axially movable compensation member at least, it adds load by extruding dish spring, in addition, the axial separation stroke of platen is to limit by the gauge device that acts between the member (for example housing and/or opposed platen) of platen and at least one axial restraint, and keep approximate constant at least, in addition, this gauge device, at least when friction clutch separates, moving axially of the relative platen of compensation device limited.

In order to improve the performance of friction clutch, particularly in order to make the Separating force change curve or must to reduce to minimum by maximum Separating force, may particularly advantageously be, the clutch disk that clamps between platen and opposed platen has friction pad, therebetween, be equipped with a so-called pad spring, it is for example open in DE-053631863.By using the clutch disk of this form, then to the operation of friction clutch, the operation to separation process is favourable especially.This be because, at the jointing state of friction clutch, the pad spring of tensioning applies a reaction force on platen, it with by extruding dish spring or to operate the power that the dish spring is applied on the platen just in time opposite.In separation process and during platen moves axially, this platen at first back pushes by the pad spring of elastic tension, meanwhile, because extruding dish spring then makes the power that is applied on the platen by this extruding dish spring also descend at the steep relatively negative characteristic curve that separated region exists.Along with the power that is acted on the platen by extruding dish spring descends, the returning place force that is applied on this platen by the pad spring also can descend.And be that difference by the extruding force of the returning place force of pad spring and extruding dish spring produces, simultaneously in order effectively to separate the necessary power of friction clutch, the axial force of the blade spring of tensioning also should be considered between platen and housing in case of necessity.After the pad relaxing of spring, that is platen from friction pad leave or clutch disk by platen and under the release conditions, necessary Separating force is mainly determined by extruding dish spring.Power-the stroke characteristic of the power-stroke characteristic of pad spring and extruding dish spring and the power-stroke characteristic of blade spring can be determined so mutually, promptly pass through under the platen release conditions, be on the low level in order to operate the essential power of extruding dish spring at clutch disk.Like this, by make pad spring characteristic curve until make by platen clutch disk discharge before and by the extruding dish spring and the close or complete equilibrium of blade spring force curve that forms or synthetic that may exist, just can be only need one very little (and under extreme case in fact necessity) extruding dish spring steering force.

When determining each spring force, also must consider by the axial force that the blade spring that acts between platen and the housing applies.In addition, when the configuration clutch, it shall yet further be noted that the locomotivity or the adjusting power of wearing and tearing sensor or wear sensor, must apply by at least one extruding force storage (as being in particular the dish spring), according to this, this power storage should be done the setting of respective strengths ground structure.In addition, advantageously be, the adjusting power of wear sensor is so to determine, promptly it should be reliably greater than because of tensioning forms the synthesis of the axial force that produces in the wedge shape of sloping platform and opposed sloping platform, this axial force can be supported by wear sensor.

The present invention relates to a kind of clutch pack in addition with friction clutch, this friction clutch has a platen, its antitorque ground but axially can limitedly be connected with opposed platen movably, at least one extrusion spring is with the direction imposed load of platen towards a clutch disk that can clamp between platen and opposed platen simultaneously, with a controlling device that wearing and tearing compensate to the friction pad of clutch disk at least is set, it by extrusion spring in fact stable power load of platen effect, this friction clutch has and is used to the operation equipment that separates and engage in addition, it by one by segregating unit for example one can turn round the withdrawal fork of arrangement at gear box casing, manipulation can axially movable separator.

What this spline structure was provided with is proposed by FR-OS2582363 with exercisable clutch pack.The operation measure of this class clutch pack can realize by piece-rate system or by separator and segregating unit, as at US-PS4368810, and those that propose among US-PS4326617 and DE-OS2752904 and the DE-OS2701999.

In having clutch pack or friction clutch that be integrated in one and the controlling device that wearing and tearing compensate to the friction pad of clutch at least, when special relevant with so-called mechanical type piece-rate system, wherein, clutch pedal move through a bar and/or Bowden cable be at least a separation support in the middle of be passed on the operation equipment of friction clutch under connecting, existing problem is, so can not guarantee owing in whole kinematic chain, have tolerance, on the segregating unit to operation equipment imposed load zone can have with operation equipment on be used for the regional identical axial position of imposed load, therefore, just may exist sizable separation stroke operational stroke lost or that be delivered on the operation equipment of friction clutch that makes to produce sizable scattering and disappearing.Performance by this lost controlling device is affected to I haven't seen you for ages, and simultaneously, under extreme case, the regulatory function of this device may not exist yet.Contingent in addition situation is, this operation equipment unallowed big stroke of passing by, may cause a undesirable adjusting thus, that is cause that friction clutch both opened no longer without doubt, perhaps make extrusion spring give tension position or the close-fitting position changes so that the active force that it applies transmission of torque without a doubt of sufficient to guarantee no longer.

Task of the present invention for this reason is, avoid these defectives and the clutch pack that an aforementioned type is set, wherein can make a controlling device that friction pad wearing and tearing are compensated have a unquestionable performance, in addition, this clutch pack can mode simple and with low cost especially be made.

The present invention of this task so realizes, a device promptly is set, it can to operation equipment relatively the axial position of this separator or segregating unit scatter and disappear or the operation equipment part that applies by separator relatively the axial position of this separator or segregating unit scatter and disappear and compensate.This device is particularly advantageous in the clutch pack that adopts a flexible program of the present invention, because this moment, at least according to the wearing and tearing operation equipment of friction pad detaching motion axially on move, therefore, just can guarantee that an in fact gapless power transmission is arranged between separating part or segregating unit and operation equipment.According to this, also can guarantee the operation equipment identical quantity of always can moving.Just can reality there be the gap in power transmission between separator and/or segregating unit and operation equipment like this.

Particularly advantageous mode can be that this compensation device is to be provided with or to act between segregating unit and the operation equipment in the axial direction.But this compensation device also can be arranged on the other position, for example is arranged between separator (Ausruecker) and the segregating unit (Ausrueckmittel) according to the mode of action.It is favourable doing like this among the present invention, and promptly separator (Ausruecker) is contained in one and is preferably on the axial guide member that gear-box side settles, for example on the guide tube of an encirclement gearbox input shaft.

Especially, require this compensation device can act on or be arranged between operation equipment and the bottom in the axial direction according to purpose having a friction clutch that on opposed platen, is fixed with housing and one in the clutch pack of the bottom of separator.In addition may for advantage be, extrusion spring by one between clutch housing and platen axially securable dish spring constitute, this dish spring has the matrix of an elastic ring and radially extension and that the form operation equipment inward tongue of matrix thus.

Adjusting in order to ensure the no problem that carries out with compensation device, may particularly advantageously be, this compensation device is at clutch pack or friction clutch jointing state, guarantee automatically or in spite of oneself the adjusting wished, and simultaneously, the operation of friction clutch is blocked automatically or in spite of oneself.

This compensation device can have an annular construction member, and it also axially rests on the operation equipment at the friction clutch jointing state.By this annular member, carry the spacing that may change between zone and the separator executing of operation equipment and just can be compensated.For the performance of this compensation device may favourable mode be, this device has adjusting sloping platform or the rising sloping platform that edges up in the axial direction, and these sloping platforms can be arranged on the member of annular simultaneously.

This rising sloping platform can with the purpose of columniform or spheroidal rolling element synergy to be used to regulate.But may particularly advantageously be that this rising sloping platform and the mating reaction of opposed rising sloping platform are because just can realize self braking under the axial tensioning situation of sloping platform by the angle of climb of correspondingly selecting these sloping platforms.Same this opposed sloping platform can be provided with on the member of an annular.

In addition, for the clutch of guaranteeing to create friction inexpensively, advantageous be that at least a portion compensation device is made of plastics.This plastics can be made with injection moulding.As plastics, particularly suitable and thermoplastic polyamide for example advantageously.

By particularly advantageous mode, this has the member of regulating sloping platform and can move vertically when clutch pack or friction clutch operation.In addition, according to the purpose requirement, the member that is equipped with rising sloping platform and opposed rising sloping platform can be in relative rotation, and simultaneously, such member can be that relative friction clutch is antitorque, and particularly clutch housing is antitorque relatively.

According to another design of the present invention, this compensation device is the structure setting so, and promptly it is seen at the detaching direction of clutch pack, similar idle running ground effect or adjusting, but the direction opposite with detaching direction is self braking.For this reason, rising sloping platform and/or opposed rising sloping platform can so be provided with, and promptly they have an angle of climb in the axial direction, and this angle is preferably in 7 ° to 11 ° the order of magnitude between 5 ° and 20 °.Be in an advantageous manner, regulate sloping platform structure setting like this, promptly exist one self to brake by frictional fit.That is, should guarantee all that under any circumstance this adjusting sloping platform has the cooperation of a self-locking, in order that the device that needn't add just can be avoided undesirable resetting.But when needed this device can be set.

In order to guarantee that this automatic compensator has the performance of no problem, according to the purpose requirement, at least one member that is equipped with rising sloping platform and/or opposed sloping platform can be spring-loading regulating on the direction.Simultaneously, this elasticity loads and can so realize by advantageous manner, and promptly the performance of all the other springs (particularly extrusion spring or dish spring and to the spring of the supporting imposed load of axial deformation) is not to be subjected to or in fact impregnable.A particularly advantageous organization plan can guarantee so that the member that promptly has rising sloping platform and opposed rising sloping platform is being regulated imposed load or tensioning on the direction by at least one at power storage that is provided with between these members such as helical spring.By the tensioning of this form, these two members (at end on observation) just are subjected to opposite direction ground extruding, that is by the power storage with to regulate sloping platform axially be to leave motion mutually.In oncoming clutch, can make compensation device no gap tensioning between the imposed load zone of operation equipment and clutch housing and/or separator vertically thus.

By particularly advantageous modification structures of the present invention, this clutch pack can have a device, is used to limit the operation equipment detaching motion at least.For this reason, a bounding means can be set, it limits at the stroke of detaching direction separator and/or segregating unit.This bounding means promptly, makes the member of a formation compensation device by favourable so structure setting of mode, according to a definite separation stroke limit on housing.But this gauge can realize so that also promptly this separator has such zone, and it just rests on the member of an axial restraint after a definite stroke.In addition, can be in an advantageous manner, this separator also has a restriction in direction of engagement, and it can be made of a bounding means equally.Press advantageous manner, this compensation device is the structure setting so, that is, at the jointing state of clutch pack, this separator is axially supporting by this device.Can also guarantee so that clutch pack has constant operational stroke, that is, the member of a formation compensation device have all work in detaching direction and direction of engagement and with the stroke gauge district of limiting area mating reaction.Can make by the compensation device member that is applied effect by separator by this member of favourable mode, simultaneously, bounding means can be arranged on the clutch housing or by this housing and make.To the qualification of clutch pack operational stroke, yet can so realize, that is, make separator vertically the member of leading corresponding bounding means is set.Best, these bounding meanss and a member mating reaction, this member spare is connected with the not rotating support ring of separator.But, make and separate stroke and can also between the member of this ring rotation such as clutch housing, finish the rotating support ring of separator and one a qualification measure on axially at least.

According to additional flexible program of the present invention, be in particular and make Separating force curve or essential maximum tearaway load reduce to minimum, may particularly advantageous mode be, a device is set, it is during separation process, by a part of operational stroke of operation equipment, just cause and little by little to reduce by friction clutch or clutch disk torque transmitted.This device can for example constitute by a so-called pad spring, and it is arranged between the friction pad of clutch disk, and clutch disk can be clamped between platen and the opposed platen.

Particularly advantageous organization plan of friction clutch of the present invention can so be realized, promptly, preferably the extrusion spring that is made of a dish spring is between two supportings that are bearing in pivotally on the housing, (in two supportings, facing to the supporting of platen by spring towards the direction imposed load of extruding dish spring), simultaneously, the maximum separation power that when friction clutch separates, in spring-loading supporting, applies by extrusion spring, under pad part abrasion condition be increase and become greater than counter-force that in spring-loading supporting, acts on or supporting force.For transmitting torque use the leaf spring element between platen and the clutch housing and/or adopt one as DE-053631863 disclosed so-called the pad under the spring situation, the power that on extrusion spring, applies by this spring so, just must when the power of determining to act in the spring-loading supporting, take in, and because these power superpose.This just means, under the situation that has enough pad spare wearing and tearing short-term regulate the Separating force that improves certainly greater than the power of power of forming by aforementioned power and relevant generation on the swing diameter of dish spring with joint efforts so that can carry out an adjusting.May meet purpose especially is, this spring-loading supporting is axially movable.By favourable mode, the characteristic curve that extruding dish spring can have a this form, promptly, the rigging position of in friction clutch, stipulating on the structure according to its (extruding dish spring), under the situation that causes unloading because of the friction pad wearing and tearing, increase by its (the extruding dish spring) power that applies and the level of Separating force curve, and on the position of a rigging position distortion of stipulating relatively or tensioning, in separation process, reduce by its maximum, force that applies.Do the structure and the configuration of this form by making extruding dish spring, just can guarantee, get discard in (friction) under the situation of existing wearing and tearing, at least friction clutch maximum separation power and act between the counter-force in the spring-loading supporting or and in the zone of supporting (Abwalz) diameter, act between the resultant force on the extruding dish spring, can be adjusted to again on the state of equilibrium.

Clutch pack or friction clutch are pressed so structure of advantageous manner, that is, this axially movable and spring-loaded supporting during standby friction clutch wearing and tearing, is moved jointly with platen.See that during the operating life of friction clutch when controlling device realized adjusting gradually or that be divided into little grade, spring-loaded supporting just can be little mobile of the enterprising Bureau sign of platen direction.Just can guarantee by this moving, spring at the platen upper support obtains an additional distortion, like this, the power (as mentioning) that is applied by its (dish spring) just descends, until till the counter-force that acts in the spring-loaded supporting or the counter-force of having mentioned that is caused and Separating force are in balance.When spring-loaded supporting was mobile, the maximum separation power of clutch or extruding dish spring just descended again.

Particularly advantageously may be, extruding dish spring so be arranged in the friction clutch, that is, it separates on the stroke (scope) in the part of clutch at least, is preferably in the power-stroke characteristic line that has a decline on whole separating ranges.Simultaneously, the rigging position of extrusion spring can be like this, and promptly in the separated state of friction clutch, in fact this extrusion spring reaches the minimum value or the lowest point point of its sinusoidal power-stroke curve.

The reaction force that in spring-loading supporting, applies, pressing advantageous manner can produce by a power storage, and it applies a constant power basically, at least, is a constant power on the regulation range of regulation.To this advantageous particularly and suitable mode be, a corresponding construction and be installed in dish spring in the friction clutch to give tensioning state.

The present invention just is not limited in above-described friction clutch, but generally can be applied in friction clutch or the clutch pack, as long as it has one at least to the controlling device of the wearing and tearing redeeming of clutch disk friction pad.

In addition, the invention still further relates to a friction clutch that is used in particular for Motor Vehicle, has a platen, its antitorque ground but can be connected with housing with limitedly moving axially, simultaneously, between housing and platen, acting on a dish spring, by it, platen can be by the direction imposed load of the clutch disk that can clamp between this platen and opposed platen towards, and clutch can engage by operation equipment (being in particular the dish languid) and separate, and also has one at least to the controlling device of the wear automatic-compensation of the friction pad of clutch disk.The friction clutch of this form is as open in DE-OS4092382.It should be guaranteed, under the friction pad abrasion condition of clutch disk, it is identical that the extruding force of friction clutch also always keeps, and by one between dish spring and platen, be provided with show and its structure to be the controlling device of two axially movable rings realize, above-mentioned two rings should be able to be revised at the axial height of platen upper support point the dish spring according to the pad wearing and tearing, therefore, the dish spring should always remain on the position corresponding with the friction pad new state.

In this clutch device, the radial spacing of the dish spring supporting between outside supporting ring and the inside supporting ring is too little.Because machining error, the machining error of the classification of ring height and particularly in the wearing and tearing that appear at during the operating life between dish spring and the supporting, so can not realize accurate an adjusting and compensation.Spacing between outside supporting and the inside supporting can not effectively enlarge, because like that, platen ventilation stroke will not dwindled with allowing and and then can not guarantee performance of clutch.

Another shortcoming is, is fixed on clutch compressing disc on the clutch housing with known manner by the blade spring, at the clutch separation state, may axial runout, simultaneously, supporting ring relatively platen in the direction adjusted of dish spring, as long as platen leaves the words of motion from the dish spring.After clutch engaged again, the dish spring had the mistake position of (part is separated), and the result is the extruding force of a variation, thereby no longer guaranteed to have separated completely.

For this reason, the other task of the present invention is, the controlling device of an aforementioned type is set, and it has simple structure and guarantees a reliable adjusting function, and can get rid of not conditioning desired.This controlling device can compact structure and cheap for manufacturing cost simultaneously.In addition, controlling device go for stretching with the compression clutch.

The present invention of this task realizes by the assembled scheme of the feature below two at least.That is:

-this controlling device has two mutual rings coaxial and that set gradually with radial spacing, this ring can move in axial direction towards the dish spring, simultaneously, they are under the effect of a controlling device, this controlling device can along the circumferential direction be rotated under the influence of moving device, as the sloping platform device of a band sloping platform and opposed sloping platform;

-this dish spring with one first radial zone at clutch state lower support (it can be called the wear compensation ring) on first ring; Simultaneously, the controlling device that can avoid belonging to it is rotated (this means that the adjusting that this wear compensation ring carries out according to the wearing and tearing of clutch disk at least can only occur on one of the dish spring position of departing from jointing state);

The controlling device of-this first ring is only discharged by a locking closure in a separation process that wearing and tearing occur and rotates; Second ring that this point occurs in previous generation is transferred after the rotation of part device and is consistent with this rotation, and this second ring is called the wear sensor ring;

The controlling device of-this second ring, bear a effect with stopping device sensor and that can prevent to rotate, the effect of this stopping device can be under the wearing and tearing and jointing state of friction clutch, eliminate according to wearing and tearing, therefore, rotate accordingly by controlling device, second ring just can realize one with wearing and tearing corresponding moving axially; And this stopping function exists between the separation period of friction clutch, requires even also can strengthen according to separation process according to purpose.

Simultaneously, controlling device is the structure setting so, that is, ring itself has sloping platform and will bear effect at the power storage of circumferencial direction effect.

The effect of this stopping device can be eliminated according to different standards, perhaps can reduce at least, for example according to the variation of a dish spring tapering that takes place because of wearing and tearing, perhaps also can be according to the installation of segregating unit, and this segregating unit require according to purpose can be by dish languid formation itself.In addition, the effect of this stopping device also can be eliminated or be reduced at least like this, that is according to the variation of the platen axial position that takes place by wearing and tearing.

Contain on the axial restraint member of (on platen) on the axially movable member that two controlling devices in the rotating ring of circumferencial direction can be arranged on friction clutch or friction clutch (as housing), and act between platen and the dish spring and be placed in therebetween the axial space according to the application.Under other applicable cases, according to the purpose requirement, controlling device can act between dish spring and the housing and be installed in its axial space.

The stopping device that can make break as an example can constitute by sensor itself.Simultaneously, particularly advantageously be, this sensor according to the disconnecting process of friction clutch, applies the effect such as the braking action of a reinforcement on second ring, simultaneously, structure can realize so that promptly, sensor is at the jointing state of friction clutch, guarantee the wear sensor ring axial regulating action (this point can may realize by rotation is provided to ring), and be to carry out according to the tapering variation of dish spring (or segregating unit) or the axial position of the relative housing of platen; Simultaneously, this sensor can be made of at least one element in the axial elasticity distortion, this element friction clutch engage and new state under or controlling device according to the adjusted state that weares and teares under, be placed in one as on the clutch member of housing, dish spring or platen and on second ring by such component; Thus, this is in rotation that the ring under the shifter effect of circumferencial direction effect carries out and just moving axially according to this has been prevented from; But, when the jointing state of friction clutch causes dish spring tapering to change by wearing and tearing, perhaps when the platen axial position changes, the support region of sensor makes the unloading of second ring at least, or even leave this ring (that is braking action is to have reduced at least), second ring can be moved device and rotate and then can move axially.

A kind of like this sensor can be made by the member of a dish spring shape by advantageous manner, and it can be fixed on this dish spring.Simultaneously, this sensor can be fixed on the side of dish spring with its radial zone, and overlaps the dish spring in the axial direction and be placed on second ring on the other side of dish spring and with one second support region with another radial zone.

This sensor, that is the member of a dish spring shape for example can also cut with scissors securely by on housing, but and be placed in one of the housing that has transition region when separating a limiting area opposite with its opposite opposed support region with second ring; Here it is, when separating, moved along the direction of housing by second ring of platen carrying, therefore, for example can turn round the braking action with sensor elastic structure installation and just be enhanced on the housing another side.

The shifter (at least for a ring) that is used to rotate regulating ring can be made of a spring.Simultaneously may favourable mode be, these springs be connected into row, and wherein, the spring-loaded that is used for first ring is at housing, and the spring-loaded that is used for second ring is in first ring.Favourable mode is that the spring of first ring is stronger than the spring of second ring simultaneously.

A simple especially organization plan is, makes first ring just allow locking closure that the rotation of second ring (and according to) rotate a spacing protuberance formation radially by second ring after a rotation takes place second ring; The relative radial lugs that on first ring, is equipped with (along the circumferential direction a seeing) backwardness with this protuberance.

A particularly advantageous structure is set to, and second ring is not rotated by locking in the separated state of clutch.This point for example can realize like this, promptly, between the stop zone on second ring and the member and between this member and second ring and engaging and separation process in, all there is an axial relative movement, and in separated state, this spacing is overcome, in order that second ring is not rotated by being bearing in to be lockable on this stop zone.In an embodiment that second ring is arranged on the housing, this device is structure so, and promptly in separated state, the dish spring is placed on second ring.When being arranged on second ring on the platen in this device, when separated state and platen moved axially, one rested on this second ring in the zone that is provided with on the housing and this second ring is pinned and do not rotate.

Can be arranged to so-called drawing clutch according to a friction clutch of the present invention, have the dish spring that acts on as single-arm lever, simultaneously, second ring directly upwards is placed in first ring the inside, wherein, two rings are axially between dish spring and housing.

Another embodiment can be so definite, and promptly under a drawing dish spring situation, second ring directly upwards is placed in first ring outside, and two rings axially place between dish spring and the platen.

Another is implemented structure and can so realize, that is, friction clutch is a so-called compression type clutch, has the dish spring that works as two arm bars, simultaneously, second ring directly upwards is placed in the inside of first ring and two rings and is arranged between dish spring and the platen on axially.Under the embodiment situation that a friction clutch is the compression type clutch, outside and two rings that second ring can be placed in first ring diametrically are located axially between dish spring and the housing.

As carrying, ring itself can be equipped with sloping platform, and opposed sloping platform can simple especially mode be made of the sloping platform in clutch housing upper punch system.Simultaneously, for friction clutch is ventilated, particularly advantageous mode may be, between each sloping platform, that is in the sloping platform crimp zone that roof shape is installed, and in the housing material, be provided with port, simultaneously, the gradient of sloping platform is so selected by the purpose requirement, promptly when clutch turns round, produces one air stream in the inner chamber of friction clutch.Verified, because air draught, operating life, particularly friction pad life-span are significantly improved.

With the structure-irrelevant of friction clutch, can particularly advantageously be that first ring (wear compensation ring) has or be configured for the pivoting support of dish spring simultaneously.

Irrelevant with the feature of referring to so far of the present invention, an inventive concept is, in the friction clutch of the described type of beginning.Controlling device is arranged between clutch housing and the dish spring.And be positioned at the axial arrangement space of these two members, simultaneously, this device can also be arranged in the radial structure space between housing and the dish spring.

One other, itself independently belonging to the inventive concept that starts described type friction clutch is, this controlling device has the ring that two footpaths upwards have spacing and mutual centering to be provided with, they each at one as be with under the same controlling device effect of the sloping platform device of sloping platform and opposed sloping platform, can be vertically move, and this controlling device can along the circumferential direction be rotated under the effect of shifter towards the direction of dish spring;

Dish spring with one first radial zone is bearing in (that is wear compensation ring) on first ring at the jointing state of clutch, simultaneously, prevents that this controlling device from rotating;

The effect that the controlling device of second ring (that is wear sensor ring) will be born a stopping device, this stopping device has a sensor, and rotates so that prevent by this sensor being bearing in the scope that is positioned on second ring away from first radial zone; The wearing and tearing that act on friction clutch and the jointing state of this device can reduce at least; And second ring and wearing and tearing move axially accordingly be realize by device for regulating rotary correspondingly and between separation period, this stopping device strengthens.

The present invention relates to general friction clutch fully, the controlling device that the particularly this wearing and tearing that are provided with at least the clutch friction pad compensate, as especially at patent application P4239291.8, P4306505.8, P4239289.6, P4231131.4, among P4243567.6 and the P4317587.2 that describe or that mention those.The theme of above-described patent application belongs to content of the present invention fully, for this reason, has concentrated these applications in first part of application materials of the application.

Realize a very low Separating force, simultaneously when attempting to have high extruding force in this clutch of regulating itself, this Separating force remains unchanged during the operating life of clutch as far as possible, and is also like this when the clutch pad weares and teares especially.

For realizing that in high extruding force a low Separating force, dish spring must have very steep power decline (curve).Because the Separating force curve should have as far as possible little fluctuation, so for this clutch, the dish spring keeps, and that is to say power-stroke curve that use can be provided, and realize one reliably and to separate (the standby stroke that adds for the tolerance tool) completely not much of that; And it is main because the dish spring has the characteristic line that falls suddenly and be again the curve of a very steep rising after a suitable short stroke.The characteristic curve of dot-dash is exactly the such spring performance line of diagramming in Figure 94, simultaneously, be positioned in the power under the clutch situation on the spring travel of about 1mm, power under pad part release conditions is to be lower than 2mm and at the 3mm place, can find out also that in characteristic line one significantly raises, simultaneously this at 3mm point place with minimum essential to separate stroke consistent.By this, not only stroke tolerance, and build-up tolerance, and also the elastic loss of the tolerance of member itself and clutch all should be taken into account.Therefore, the additional travel fluctuation that also tolerance owing to piece-rate system should be caused is listed in, and like this, essential spring travel extends to 3.5mm at least in diagram.This means, not only be that a different Separating force of strong row rises, and for example in patent application P4239291.8, had under the clutch situation of sensor dish spring that the regulating ring of controlling device may carry out a undesirable adjusting.

The other task of the present invention is for this reason, avoids above-mentioned shortcoming, that is to say, a clutch is set, and it (comprising possible tolerance), has an alap and constant as far as possible Separating force in whole separation strokes.Simultaneously, in possible maximum separation stroke, avoid one not allow or the rising of undesirable power.In addition, the manufacturing that itself and a member also should be set can simply reach the cheap clutch of realizing, and these members can also have light as far as possible specification.For realizing this point at least in part, in conventional clutch with high Separating force for reach in the piece-rate system between clutch and pedal still can pedal operation power, for example use the pneumatic or servo auxiliary device of expensive hydraulic pressure, perhaps be called the dead point system.

But this solution has complete conclusive defective, promptly, huge clutch separation power imports in the operation system by separation support, thus, not only in clutch, and the frictional loss of additional drawback all appears becoming in (owing to high Separating force requires very big elasticity) in operation system, like this, clutch pack not only, and whole operation system comprises for example axially mounting of motor, all must have the power load of enough sizes to be applicable to that these are very high, thereby, relatively costly member can only be used.For this reason, task of the present invention is, also will eliminate the defective of this system.

This task is so to realize according to the present invention, promptly uses a dish spring, and its power between Figure 94 medi-spring travel point 1 and 2 descends to having with previously described approximately identical power and descends.This dish spring has a power minimum value that is positioned at obviously low (deeply), simultaneously, and this minimum force even can promptly can be negative value less than zero.This dish spring as finding out from fine line among Figure 94 like that easily, and has a spacing greater than 2mm between two point of intersection of 10000N line, and this is with opposite with the spring of dot and dash line description, has the only spacing of about 1mm between the point of intersection of it and 10000N line.This just means, the total stroke length in this power scope, and under the sulphur spring situation of the characteristic line with fine line, it is big like this to be actually twice.But the clutch with this characteristic line (that is corresponding with fine line) is for clutch operating, have very big defective, because, in the first stroke zone, to a positive active force occur, after this be exactly the decline toward negative power, is again a rising to positive power then.This means,, corresponding power can in piece-rate system, occur and change, and this point can not be controlled without doubt by pedal by separating stroke.

Even people use such dish spring, wherein, this minimum value is not to descend as having dark (low) the dish spring that fine line describes at one, but under this dish spring situation, the power of minimum value also is positioned at and is higher than zero a little, that is always remain on positive interaction power, so the clutch performance then because very strong power changes, causing when separating can only be to be difficult to control.By another step of the present invention, that is use at least one additional so-called counterbalance spring (as also describing in detail this later), it mainly acts in the scope of clutch disc spring force minimum value, and so, this strong power descends, and this has been avoided (that is characteristic line of describing with fine line in Figure 94), according to this, essential separation has steadily reached, and simultaneously, that is the prolongation curve branch of the characteristic line of being described by fine line just has been utilized, simultaneously, unallowed power decline has been avoided.

Additional features content of the present invention and meet flexible program and the advantage that purpose requires can propose from the description of following Fig. 1 to 93.

The present invention proposes a kind of friction clutch that is particularly suitable for Motor Vehicle, has a platen, this platen is not rotating but can do axially that limited mobile mode links to each other with shell, a dish spring that produces extruding force is axially compacted between shell and platen simultaneously, this dish spring is on the one hand around the pivoting support revolution that is bearing on the shell, on the other hand platen is pressed to a direction between platen and the opposed platen as the clutch disk that clamps of flying wheel, one of them can compensate and be carried continuously by an advancing means the wearing and tearing of the friction pad of clutch disk at least, and act on that the pivoting support that is being supported by shell in the automatic control tegulatingdevice can move in the axial direction between housing and the dish spring, and the dish spring is in the direction towards pivoting support under the effect of support force;

The dish spring constitutes the characteristic curve that successively decreases in its working area;

The dish spring only is to be supported by the power transfer mode opposite with Separating force;

Supporting force and disc spring force are to mate so each other, promptly on the mounting point of dish spring regulation and when the tapering variation not occurring because of wearing and tearing, in the separation stroke of dish spring, supporting force is greater than the reaction force to supporting force that is produced by the dish spring, having under the situation of wearing and tearing when the tapering of dish spring changes, separating supporting force in the part area of stroke less than the power opposite that produces by the dish spring with supporting force at the dish spring;

Supporting force is by a power storage at least, and for example spring forms, the adjustment period that abrasion condition is carried out between this supporting force can change the configuration of the supporting of dish spring or case side;

Controlling device is axially disposed between dish spring and the lid;

Controlling device has the elevation surface as sloping platform;

Supporting force is formed by dish spring type parts;

Be supported on the dish spring at the dish spring that produces supporting force on the radial height of axially movable supporting;

The dish stage clip is bearing between two supportings of shell side pivotally, wherein props up to afford the elastic load that pressing plate is applied towards the direction of dish stage clip;

Can move axially by the spring-loading supporting of supporting force;

Spring-loading supporting produces and the Separating force of dish stage clip is reduced when mobile

Spring-loading supporting moves to the dish stage clip till Separating force that produces in the supporting and the reaction force that is supporting formation reach equilibrium of forces always;

Load the reaction force that forms in the supporting in elasticity and produce by the power storage, this power storage has the power of substantial constant in the regulatory region that sets;

The power storage that produces supporting force plays sensor;

Load in elasticity on the movement direction of supporting, reverse supporting set on the dish stage clip can move axially to the direction of platen, but brakes on opposite direction;

The advancing means that controlling device is carried continuously is a spring;

Controlling device has a relevant with it ring part, and this ring part is subjected to the axial loading of dish stage clip when friction clutch is in jointing state;

Controlling device has the adjusting sloping platform of axial rising;

Regulating sloping platform is arranged on the ring part;

Have an oppositely supporting on the ring part;

Rising sloping platform and corresponding opposed rising sloping platform interact;

Have opposed rising sloping platform on the ring part, ring part is arranged between the parts and housing that have the rising ramp platform;

Opposed rising sloping platform is formed directly in the radially extension area of shell;

But controlling device unrestricted motion on the detaching direction of friction clutch, and on the direction opposite with detaching direction automatic brake;

At least the sloping platform that rises has a lift angle, and this lift angle is 4 °-20 °, is preferably in 5 °-12 ° magnitude;

The rising sloping platform has a lift angle, and this lift angle carries out friction engagement by the opposed rising area of rising sloping platform and another parts and produces automatic brake;

Apply elastic load adjusting on the direction at least to parts that have the rising sloping platform and/or the parts that have opposed rising sloping platform or an opposed rising area;

Controlling device has a plurality of parts of movably regulating;

Controlling device is revolution type (Figure 12,13);

Controlling device is braked (Figure 12,13) according to revolution;

When surpassing certain boundary, revolution makes the controlling device locking;

Under idling speed or revolution controlling device is worked when being lower than idling speed;

In fact controlling device begins to work when revolution is zero;

Having rising sloping platform and/or opposed rising sloping platform or opposed angled section and can be subjected to elasticity with respect to the part that shell moves on the controlling device loads;

Elastic load is generation power on tangentially;

The radial outside area supporting of the sensor spring of generation reaction force is on shell;

On shell, be provided with a supporting area that is suitable for forming the sensor spring of reaction force;

Pad spring or pad spring substitute material are arranged between the friction pad of clutch disk;

The pad spring that is provided with between the friction pad of clutch disk has a stroke-force characteristic curve, the stroke-force characteristic curve similar (Figure 18) of the power that this curve produces on pressing plate to the dish stage clip in the springing stroke of pad spring;

When friction clutch was in separated state, making dish stage clip or the needed power of friction clutch work was-150 to 150Nm magnitudes;

After clutch disk discharges, make the dish spring transfer negative power-flight distribution curve (Figure 18) to from positive power-flight distribution curve by opposed platen.

A kind of friction clutch that is applicable to Motor Vehicle, has a platen, this platen can not rotate but can do and axially limitedly link to each other with shell movably, between shell and platen, be provided with simultaneously an operating device and a force-storing device at least, can apply towards in a load between itself and the opposed platen to platen by them as the clutch disk direction that clamps of flywheel, wherein has the controlling device that an energy compensates the friction pad occurring wear of clutch disk at least, this controlling device comprises a wear compensation device that is arranged between operating device or force-storing device and the platen, compensation device between operating device or force-storing device and platen carries out corresponding axial adjustment to the wearing clearance of friction pad, after the corresponding adjusting that the actual wear state of friction pad is done is finished, wear compensation device is limited on its regulatory function by the mechanism that is located on the platen;

The dish spring of an axial compression is set between shell and platen, and this dish spring can turn round around a ring-shaped bearing of shell support and have an annular matrix that is used to form force-storing device, and the tongue that extends radially inwardly stretches out from this annular matrix;

The limting mechanism of compensation device is made of a wear sensor at least, and this wear sensor has a sensing element that oppositely moves with platen, and this sensing element is by being provided with the separation stroke that the axial restraint parts limit platen;

Sensor element can move axially and by automatic regulating apparatus and axially movable parts for example platen link to each other, but also can be by at least one Axial Mounting Part such as shell being set and/or opposed platen is adjusted it;

Movably sensor element has a contact area, and this contact area interacts when friction clutch separates with the opposed contact area of the compensating unit of compensation device;

Movably sensor element is bearing on the platen by controlling device;

Compensation device comprises a support unit that is used for force-storing device, and between this support unit and platen, being provided with a compensation device, this compensation device weares and teares automatically to support unit when friction clutch separates and adjusts and Braking mode during in clutch;

Supporting can move axially leaving on the direction of pressing plate, towards pressing plate axially on then produce braking;

Compensation device has the effect that can move freely when friction clutch separates, and when friction clutch engages automatic brake;

Compensation device has a compensating part that is made of ring part;

Ring part is supported on the platen opposite by sloping platform;

Sloping platform and opposed sloping platform interact;

Sloping platform and opposed sloping platform compress mutually by spring;

Annular element forms the sheet component with hole, U-shaped cross section, is equipped with to be distributed in wedge-shaped member on the periphery and that be made of sloping platform in the free space of parts;

Wedge-shaped member is lockable with respect to annular element and does not rotate;

Wedge-shaped member can produce with respect to annular element and move axially;

Opposed sloping platform is made of wedge, this wedge to small part snap in by annular compensating part around free space in and can rotate with respect to platen and compensating part;

Compensating part is lockable with respect to platen and does not rotate;

Opposed sloping platform is flexibly loaded towards the sloping platform direction;

Elastic load is that for example helical spring forms by the spring of pressurized between the parts that constitute sloping platform and opposed sloping platform;

Constitute parts section axial clamping at least between parts that constitute sloping platform and compensating unit of opposed sloping platform;

At least the petiolarea at the spring that sloping platform and opposed sloping platform are compressed should lead by the parts that constitute sloping platform and opposed sloping platform;

The parts that constitute sloping platform and/or opposed sloping platform are made of heat insulation and heat-resistant material;

The parts that form sloping platform and/or opposed sloping platform are by heat-resistant material, and for example thermoplastic or thermosetting plastics constitute;

The material that constitutes sloping platform parts and/or opposed sloping platform parts has high coefficient of friction;

During clutch separation, the stroke of dish spring is greater than the part of leaving of the platen that is limited by limting mechanism in the platen that is subjected to the effect of dish spring loads the diameter region scope;

Compensation device all unloads in each separation process;

Compensation device has two sloping platform members that are adjacent to mutually, and wherein, sloping platform member can not rotate and another sloping platform member can not be with respect to can being reversed by the compensating part that force-storing device loads with respect to platen, but compensating part can rotate with respect to platen.

A kind of friction clutch that is specially adapted to Motor Vehicle, has a platen, this platen can not rotate but can do and axially limitedly link to each other with shell movably, while dish-shaped stage clip axial compression between shell and platen, this dish spring can rotate around an annular pivoting support that supported by shell on the one hand, apply towards one between platen and the opposed platen as the clamped clutch disk direction ground of flywheel load to platen on the other hand, but also has a controlling device that the friction pad occurring wear on the clutch disk is compensated, it is characterized in that, between pressure dish spring and platen, be provided with a wear compensation device, this compensation device has one at least can axially movable compensating unit, the dish stage clip loads to compensating unit, in addition, the axial separation stroke of platen is limited and keep approximately constant at least by the limting mechanism that between platen and at least one Axial Mounting Part, forms, and at least when friction clutch separates, limting mechanism limits with respect to moving axially of platen compensating unit.

A kind of friction clutch that is particularly suitable for Motor Vehicle, has a platen, this platen not rotating but the mode that can make axial finite displacement link to each other with shell, a stage clip is set between shell and platen simultaneously at least, this stage clip can to platen apply towards between platen and opposed platen with a load as the clamped clutch disk direction of flywheel, and has a controlling device that an energy compensates the friction pad occurring wear of clutch disk, this controlling device produces the power load of a substantial constant to platen by stage clip, friction clutch also has and is used to engage and the operating device that separates and a damping device, in separation process, this damping device makes the moment by friction clutch or clutch disk transmission descend gradually on the part area of operating device operational stroke;

Friction clutch has a damping device, and in separating stroke, this damping device produces on the partial distance that moves axially stroke in the platen district that loaded by stage clip the moment of friction clutch transmission is descended gradually;

This damping device is arranged in the power bang path between the fixed area of the shell on operating device or stage clip and the opposed platen;

This damping device is arranged in the power bang path between the rubbing surface of operating device or stage clip and platen;

This damping device is axially disposed between the friction pad of clutch disk;

This damping device can produce axial elasticity between clutch component flexible, therefore damping device can be set like this, promptly when clutch is opened, make the power that acts on the damping device for minimum, and when clutch is closed, make the power that acts on the damping device increase to maximum gradually, and this increase should occur on the part area that engages stroke at least;

Damping device causes being reduced gradually on about 40-70% operational stroke of operating device at least or increase gradually by the moment of friction clutch transmission;

Stage clip has the power-flight distribution curve that successively decreases at least on the part area of friction clutch separation stroke;

Stage clip is made of the dish spring, and this dish spring can wind the annular pivoting support that is supported by shell on the one hand and rotate, and loads to platen on the other hand;

The dish spring has annular solid, and the tongue of a formation operating device radially inwardly stretches out from annular solid;

Dish spring between two supportings is bearing on the shell pivotally;

The dish spring has sinusoidally power-stroke characteristic curve, and be at friction clutch under the state of joint, the drive point of dish spring is in since the decline characteristic curve district that the first maximum, force value forms, and the maximum, force value of this dish spring and the force rate between the minimum force value that forms thereafter are 1: 0.4-1: 0.7.

A kind of Motor Vehicle that is particularly suitable for the friction clutch of Motor Vehicle, clutch can be operated by the piece-rate system that acts on the operating device, and wherein piece-rate system has clutch pedal, and the structure of this pedal is similar to gas pedal.

A kind of preassembled clutch pack, has pressing plate, this platen is not rotating but can make limited axially movable mode and link to each other with opposed platen, wherein at least one stage clip that is bearing on the shell applies load towards the clutch disk direction that can clamp to platen between platen and opposed platen, the controlling device that also has an abrasion that occurs at least can friction pad to compensate in addition to clutch, this controlling device produces the power load of substantial constant to platen by stage clip, this clutch pack has and is used to engage and the operating device that separates, and has a damping device, this damping device has an elastic component that in series is provided with stage clip at least, in separation process, damping device causes being reduced gradually by the moment of clutch disk transmission on the part area of operating device operational stroke.

A kind of clutch pack, has platen, this platen can not rotate but can do and limitedly link to each other with opposed platen with axial motion, wherein at least one stage clip applies load towards the clutch disk direction that can clamp to platen between platen and opposed platen, has a controlling device that can compensate occurring wear on the friction pad of clutch disk at least in addition, this controlling device applies substantially invariable power load by stage clip to platen, and this friction clutch also has and is used to engage and the control mechanism that separates and a damping device, in separation process, damping device causes being reduced gradually by the moment of friction clutch or clutch disk transmission on the part area of operating device operational stroke, in addition, opposed platen is mass block parts in the double quality blocks flywheel, its quality can overcome the influence of rotating the oscillation damping spring and produce relative rotation each other, and wherein another mass block parts link to each other with the live axle of internal-combustion engine;

Shell and the flywheel loaded components that is made of opposed platen form being rotationally connected that non-destruction can not free;

Damper is arranged on the radial outside of clutch disk external diameter.

A kind of and internal-combustion engine uses together, the clutch pack that is particularly useful for Motor Vehicle, it comprises a friction clutch that has platen, platen is not rotating but can make limited axially movable mode and link to each other with opposed platen, have at least one stage clip in addition, this stage clip applies the load of clamped a clutch disk direction as flywheel between platen and opposed platen to platen; Friction clutch has a controlling device that can compensate occurring wear on the friction pad of clutch disk, this controlling device is producing substantially invariable power load by stage clip during the operating life on platen, also have and be used to engage and the operating device that separates, comprise a damping device in addition, this damping device makes on the part area of operating device operational stroke the moment by friction clutch or clutch disk transmission reduce gradually in separation process, wherein friction clutch is connected with the live axle of internal-combustion engine by an axial elasticity spare, the intensity of elastic component is to set like this, the axial vibration that promptly utilizes elastic component on clutch, to produce by live axle, swing is vibrated or flexure vibrations reduce or be suppressed to certain ratio, so just can guarantee friction clutch, especially its controlling device plays one's part to the full;

The intensity of parts is to set like this, promptly props up the required steering force of clutch separation by parts clutch pack is not moved axially basically;

Damping device has an elastic mechanism, the setting that is connected with stage clip of this elastic mechanism;

Opposed platen links to each other with the live axle of internal-combustion engine by damper.

A kind of transmission device that is specially adapted to Motor Vehicle, being located at the operation according to reduction gear between drive motor and the reduction gear by automatic or automanual reduction gear and one controls the controlled friction clutch of (or adjusting) and constitutes, this friction clutch dish has a platen, platen is rotatable but can do axially limitedly to connect together with an opposed platen that can link to each other with the live axle of drive motor movably, also comprise at least one stage clip, this stage clip applies towards the load of one between platen and opposed platen the clamped clutch disk direction as flywheel to platen, has a controlling device that can compensate occurring wear on the friction pad of clutch disk at least simultaneously, this controlling device can produce substantially invariable power load to platen by stage clip, have in addition and be used to make friction clutch to engage and the operating device that separates and a damping device, this damping device makes the moment of friction clutch or clutch disk transmission reduce gradually in separation process on the part area of operating device operational stroke;

Stage clip forms the power-stroke characteristic distribution curve that successively decreases at least on the part area of separating stroke;

Damping device reduces the moment of friction clutch transmission gradually or increase to be gradually to work on the 40-70% that is approximately operating device and/or platen operational stroke.

A kind of clutch pack, has a platen, this platen can not rotate but can do and axially limitedly link to each other with an opposed platen movably, wherein at least one stage clip applies load towards the clamped clutch disk direction between platen and opposed platen to platen, in addition, also has a controlling device that can compensate occurring wear on the friction pad of clutch disk at least, this controlling device applies substantially invariable power load by stage clip to plate, friction clutch has and is used to the operating device that separates and engage, this operating device can be operated by the axially movable separator of separating mechanism by means of one, simultaneously operating device should in separating stroke, produce according to the wear extent of abrasion pad at least move axially and also the power bang path between separating mechanism and operating device in an energy is set moving axially of operating device is carried out the damping device of approximate equilibrium at least;

Balance and buffer device is located between separator and the operating device;

Friction clutch has a shell that can be fixed on the opposed platen, and for example the steel plate lid has a base plate that separator is moved on the shell, and balance and buffer device can be between operating device and base plate axial compression;

But stage clip is the dish spring by axial compression between clutch outer member and platen to be constituted, and this dish spring has a flexible annular matrix and the tongue of the formation operating device that extends radially inwardly from matrix;

Balance and buffer device has the adjustment sloping platform of rising in the axial direction;

Adjusting sloping platform is made of the rising sloping platform that is provided with on ring part at least;

Adjust sloping platform and comprise opposed rising sloping platform, this opposed rising sloping platform and rising sloping platform interact;

Opposed rising sloping platform is located on the ring part equally;

Having the parts of adjusting sloping platform can produce mobile in the axial direction;

The parts that have rising sloping platform and opposed rising sloping platform can reverse each other relatively;

One of parts with sloping platform or opposed rising sloping platform can not rotate relative to friction clutch;

Adjust sloping platform and have lift angle, this lift angle can form automatic brake by the friction engagement of adjusting sloping platform;

Adjusting the lift angle that sloping platform has is between 4 ° to 20 °, preferably 5 °-12 ° magnitude;

At least one have parts modulated perfect square that rising sloping platform and/or one has an opposed rising sloping platform to the elastic load effect;

The parts that have the parts of rising sloping platform and/or have an opposed rising sloping platform are subjected at least one and are arranged on force-storing device between two parts, and for example helical spring is being adjusted load or the impacting force that applies on the direction;

It is in order to limit separating stroke that damping device is set;

Damping device has a bounding means at least;

Limit stoper forms between separator and clutch lid;

Separator has a clutch separation supporting and bounding means can be movable between supporting ring that rotates with friction clutch and clutch lid;

Limit stoper is arranged between the separator conduit of establishing on the back flow side and separator;

Be provided with mechanism, this mechanism makes the moment of friction clutch or clutch disk transmission reduce gradually in separation process on the part area of operating device operational stroke;

The stage clip that is made of the dish spring is bearing between two supportings on the clutch outer member pivotally, be subjected to platen by two supporting stage clips and move the elastic load that applies to the direction of stage clip, wherein when friction clutch separates, the dish spring can increase when friction pad weares and teares and surpass in the power that produces in the spring-loading supporting and acts on elasticity and load power in the supporting;

Spring-loading supporting can move axially;

When the Separating force of dish stage clip increased, elasticity loaded supporting and moves to the direction of platen;

When elasticity loading supporting was mobile, the Separating force of dish stage clip reduced;

The displacement distance that elasticity loads supporting should make the maximum separation power that acts in the supporting will separate the force characteristic curve that has decline on the part area of stroke at least with the reaction force dish stage clip that generation is gone up in supporting;

The reaction force that produces in spring-loading supporting is formed by force-storing device, and force-storing device has the constant power of substantial constant on set adjustment region;

Have axial elasticity or movably support and load by the dish spring that uses as force transducer.

A kind of friction clutch that is specially adapted to Motor Vehicle, has platen, this platen can not rotate but can do and axially limitedly link to each other with shell movably, between shell and platen, be provided with simultaneously a dish spring, by this dish spring platen is subjected to towards the load of the clamped clutch disk direction between platen and opposed platen, and clutch can and separate by the operating device joint, also has a controlling device that can compensate automatically occurring wear on the friction pad of clutch disk at least, it is characterized in that, controlling device has two and is located at same parts (lid, platen) on and at the ring that radially is spaced from each other certain distance, two rings are in controlling device, for example can move axially towards the dish spring under the effect of sloping platform formula device, regulating device then can reverse producing on tangential under the effect of conveying equipment;

When friction clutch was in jointing state, the dish spring also stoped the controlling device generation to be reversed with first ring that its first radial portion supports as the wear compensation ring thus;

Second ring is that the regulating device of abrasion detection ring is provided with a stopping device that has sensor and can avoid reversing, the effect of stop will be cancelled when friction clutch is in jointing state and wearing and tearing take place, and can second ring be produced with the corresponding axial displacement of wearing and tearing by suitably reversing of controlling device thus and then make stopping device bring into play its effect in separation process;

When appearance is worn and torn in the separation process, after the rotation of second controlling device of encircling that correspondingly takes place in advance, in order to make the first controlling device rotation that encircles and it to be discharged from stopping device;

Ring itself has sloping platform and be provided with the force-storing device that works on tangentially;

When changing because of wearing and tearing, the gradient of dish spring makes the effect cancellation of stopping device;

When changing, the axial position that makes platen because of wearing and tearing makes the effect cancellation of stopping device;

Controlling device generation effect between clutch lid and dish spring;

Controlling device is the generation effect between dish spring and platen;

In the axial arrangement space, controlling device is arranged between clutch cover plate and the dish spring;

In the axial arrangement space, controlling device is arranged between dish spring and the platen;

Two rings by torsion proof in the friction clutch but can do axially movable parts for example platen support;

Two rings are by for example cover plate support of the Axial Mounting Part in the friction clutch;

Sensor itself constitutes stopping device;

A kind of friction clutch is characterized in that, the effect of stopping device strengthens with the separation process of friction clutch relevantly;

When friction clutch is in jointing state, permission is made of the extension member that at least one has axial elasticity at the wear sensor that reverses and the abrasion detection ring is axially adjusted with respect to the gradient or the axial position variation of cover plate according to platen on tangential by controlling device, when friction clutch is in jointing state and new state, under the state that controlling device adjusts accordingly wearing and tearing, this elastic component is bearing on the clutch component and second ring with such component, what promptly the effect of inertia by the feedway that works on tangential and ring prevented that the environment-development life from reversing and causing thus moves axially, and when friction clutch was in jointing state and because of wearing and tearing the axial position of the gradient of dish spring or platen is changed, the Support of sensor was reduced pressure second ring at least or is mentioned and make ring reverse and produce thus from feedway and moves axially;

Sensor is made of leaf spring or dish spring type elastic member;

Sensor is made of flexible parts with precompression;

Sensor is fixed on the dish spring;

The radial portion and the dish spring of sensor are hinged, and another radial portion is bearing on second ring;

Sensor with its 3rd regional additional support on the dish spring;

Sensor is fixedly hinged at lid, and links by the limiting area of shell on second ring on opposite, Support, and is relative with the Support with the distance L that can overlap when separating herein;

Sensor is arranged on the abrasion detection ring;

The sensor that has a wear detector by two parallel and in the axial direction each other the ring of elastic tension constitute;

The abrasion detection ring is made of elastic member;

The abrasion detection ring is made of corrugated spring forming spare;

The conveying equipment that is used at least one regulating ring is made of spring;

Spring-loaded is having on the parts of ring;

Two spring shackles are connected in series;

Be supported on the ring bearing parts with one of first or second ring corresponding spring, and with first or second ring in another encircles corresponding spring and is supported on the ring;

Ring is supported on the spring of the power of a spring on the ring bearing parts greater than another ring;

By be located on second ring and make opposite opposed spacing preiection and constitute this braking device from cutting the projection that looks up with the first ring heel, it second environment-development give birth to rotate after, just discharge first and encircle and rotate;

When clutch was in separated state, second ring was lockable and can not reverses;

When friction clutch is in jointing state, have an axial distance L that can overlap between the limiting area of second ring and parts in separated state, axial relative movement can take place between the parts and second ring;

The dish spring encircles second in the state lower support of separating rotation;

Second ring is pressed to lid under separated state;

Be arranged on the ring of second on the platen and under separation and axially movable state, press to the dish spring;

Being arranged on the ring of second on the pressing plate presses down to shell in the separation and the state that moves axially;

Distance L 1 between dish spring supporting on the axial distance L2 of first ring and second ring and first ring and the dish spring on the relative parts support is in a ratio of L2＞30%L1;

Radial distance between first ring and second ring is approximately equal to the first dish spring supporting that encircles and the distance between the dish spring supporting on the relative parts at least;

The approximate at least ventilation stroke (L1) that is equivalent to clutch pressure plate of the springing stroke of sensor (L);

The ventilation stroke S of the springing stroke S of sensor and clutch pressure plate _{The ratio of D be S＜-SD}* (L2: L1) (Figure 72);

So-called draw-off type clutch has had the dish spring of single-arm lever effect and has been arranged on second ring of the first ring radially inner side, and two rings all be arranged between dish spring and the lid axially on;

So-called draw-off type clutch has had the dish spring of single-arm lever effect, and second ring is arranged on the radial outside of first ring, wherein two rings all be arranged between dish spring and the platen axially on;

So-called pressure type clutch has had the dish spring of double-arm lever effect and second ring has been arranged on the radially inner side of first ring, two rings all be arranged between dish spring and the platen axially on;

So-called pressure type clutch has had the dish spring of double-arm lever effect and the radial outside that second ring is arranged on first ring, and wherein two rings all be arranged between dish spring and the dish axially on;

The opposed sloping platform of controlling device is to be made of the sloping platform that is compressed on the clutch lid;

Between each sloping platform on the lid, be provided with through hole;

The opposed sloping platform of controlling device is to be made of the sloping platform that is formed on the platen;

Sloping platform on the platen forms by suppress each sloping platform on a plate-like piece;

At platen with have and be provided with the passage that radially extends between the plate-like piece of sloping platform;

Ring is that the wear compensation ring has the pivoting support that is used for the dish spring simultaneously;

On clutch with pressuring method work, controlling device is arranged between dish spring and the lid, a side that allows regulating device to rotate thereon on the dish spring is supported by support spring;

When clutch separation, supporting dish spring provides a pivoting support position in the phase I of separating stroke for the dish spring;

After the outer rim of dish spring kept flat on the detection ring and separating in the second stage of stroke bearing and turning on the detection ring, the dish spring was mentioned and is made supporting dish spring produce resiliently deformable in the direction of platen from the supporting of first ring;

Controlling device is being arranged between dish spring and the platen in clutch, platen is by spring and lid tension.

A kind of friction clutch that is specially adapted to Motor Vehicle, it has platen, this platen can not rotate but can move axially with an Axial Mounting Part for example shell link to each other, between shell and platen, acting on simultaneously a dish spring, can apply towards the load of the clutch disk direction that between platen and opposed platen, can clamp to platen by the dish spring, and can make clutch and separate by control mechanism, also has at least the controlling device that can compensate automatically occurring wear on the friction pad of clutch disk, it is characterized in that controlling device is arranged between clutch lid and the dish spring.

A kind of friction clutch that is particularly suitable for Motor Vehicle, has a platen, this platen can not rotate but can move axially with an Axial Mounting Part for example shell link to each other, between shell and platen, acting on simultaneously a dishful of spring, can apply towards the load of the clutch disk direction that between platen and opposed platen, can clamp to platen by the dish spring, and can make clutch and separate by control mechanism, also has at least the controlling device that can compensate automatically occurring wear on the abrasion pad of clutch disk, it is characterized in that, controlling device has two rings that radially separate and that be provided with one heart mutually, two rings under the effect of the sloping platform device that regulating device for example is made of sloping platform and opposed sloping platform can the dish spring axially on move, controlling device can rotated on tangential under the effect of feedway, when clutch is in jointing state, it is on the wear compensation ring that first radial portion of dish spring is supported on first ring, and stop controlling device to be reversed thus, second ring is that the effect of the controlling device of wear compensation ring can be interrupted by stopping device, this stopping device has a sensor, and can be by will on second ring, preventing that regulating device from reversing in a zone of leaving first radial portion from self-supporting, when wearing and tearing and friction clutch occurring and be in jointing state, the effect of this stopping device should reduce at least, can second ring be produced with wearing and tearing by suitably reversing of controlling device thus moves axially accordingly, and when clutch was closed, the effect of stopping device strengthened.

The particularly suitable friction clutch in one place, this clutch is particularly useful for Motor Vehicle, this clutch has a platen, platen can not rotate but can do and axially limitedly link to each other with shell movably, between shell and platen, acting on simultaneously a dish spring, can apply load to platen by this dish spring towards the clutch disk direction that can between platen and opposed platen, clamp, and can make clutch and separate by an operating device, can be when on the friction disk of clutch disk, wearing and tearing occurring at least but also have to its controlling device that compensates automatically, it is characterized in that, combined to two features that the major general is following, that is:

Controlling device has the ring that two footpaths upwards are spaced from each other setting, two rings controlling device for example under the effect of sloping platform device can the dish spring axially on move, controlling device can rotated on tangential under the effect of feedway,

When clutch was in jointing state, it was on the wear compensation ring that first radial portion of dish spring is supported on first ring, and prevented the controlling device rotation thus,

Second ring is that the effect of the controlling device of abrasion detection ring can be interrupted by the stopping device that possesses sensor and prevent to reverse, can be cancelled when wearing and tearing and clutch are in jointing state appears in the acting on of this stopping device, can second ring be produced with wearing and tearing by suitably reversing of controlling device thus moves axially accordingly, stopping device is played a role

When occurring wearing and tearing along with the continuation of separation process, the controlling device of first ring discharges from braking device in order to reverse, and that carries out after this and correspondingly before this that second controlling device of adjusting ring carried out reverses.

A kind of particularly suitable friction clutch that uses with clutch disk, it is adapted to Motor Vehicle especially, wherein clutch has a rotating support that is used for the dish spring, the dish spring applies towards the load of pressure disk and opposed platen direction to axially movable platen, and has a device that can compensate the wearing and tearing of friction plate at least, it is characterized in that, at least approximate from clutch disk on detaching direction no longer or only apply the stroke of inappreciable load to platen, the power of dish spring and another force-storing device is superimposed, and the distribution curve of making a concerted effort that obtains is thus compared with the power distribution curve of dish spring remain basically stable;

Clutch disk is one and has the clutch disk of " pad spring ";

Another force-storing device is an all-in-one-piece in clutch " counterbalance spring ";

Counterbalance spring is a dish spring;

At least approximate from clutch disk on detaching direction no longer or only apply the stroke (release travel) of inappreciable load to platen, counterbalance spring has the power-flight distribution curve of a bending, this curved section all deviates from mutually with the bending of the power-flight distribution curve of dish spring, and for example direction is opposite.

Fig. 1 is the view of friction clutch of the present invention;

Fig. 2 is the sectional view of II-II along the line among Fig. 1;

Fig. 3 is the regulating ring that is applied to friction clutch among Fig. 1 and Fig. 2;

Fig. 4 is the sectional view of IV-IV along the line among Fig. 3;

Fig. 5 is the supporting ring that is applied to friction clutch among Fig. 1 and 2;

Fig. 6 is the sectional view of VI-VI along the line among Fig. 5;

Fig. 7 A and Fig. 7 B are one rotatory force are acted on spring on the regulating ring;

Fig. 8 to 11 is sketches of different qualities curve, therefrom, can obtain each spring element of clutch of the present invention and the synergy of regulating element;

Figure 12 and 13 is another organization plans of friction clutch of the present invention, and wherein, Figure 13 is along the sectional view of XIII line among Figure 12;

Figure 14 is the regulating ring view that is applied to friction clutch in Figure 12 and 13;

Figure 15 to Figure 17 is the friction clutch detail drawing of another band balanced protection device;

Figure 18 and Figure 19 are the sketches of different qualities line, therefrom can obtain to push dish spring and the flexible synergy of liner and by draw the effect that produces on the clutching force curve of friction clutch;

Figure 20 A is the partial view of a friction clutch among the present invention;

Figure 20 B is the partial view along arrow A direction among Figure 20 A;

Figure 21 is the sectional view of XXI along the line among Figure 20 A;

Figure 22 is a regulating ring partial view that is applied to friction clutch in Figure 20 A and 21;

Figure 23 and Figure 24 are the other flexible programs of friction clutch of the present invention;

Figure 25 is a regulating ring view, and it can be applicable to the friction clutch among Figure 12 and Figure 13 or Figure 20 A to Figure 21;

Figure 26 to Figure 29 is the friction clutch flexible program that replenishes;

Figure 30 to Figure 32 is another organization plan detail drawing of friction clutch, wherein, Figure 31 be among Figure 30 along the partial view of arrow A, and Figure 32 is by the sectional view of arrow B-B among Figure 31;

Figure 33 is a view of friction clutch of the present invention;

Figure 34 is the sectional view of II-II along the line among Figure 33;

Figure 35 is the sectional view of III-III along the line among Figure 33;

Figure 36 is the sectional view of IV-IV along the line among Figure 33;

Figure 37 is a regulating ring view that is applied to friction clutch in Figure 33 and 34;

Figure 38 and Figure 39 are two other organization plan views of friction clutch of the present invention;

Figure 40 is the flywheel of a band torque-vibration damper and friction clutch of the present invention, and it is set to two mass blockes by branch,

Figure 41 and Figure 42 are torque transmitters with friction clutch of the present invention,

Figure 43 is the clutch pack sectional view that is provided with according to structure of the present invention;

Figure 44 be magnifiation in depth just with the illustrated balanced protection device in cross section,

Figure 45 is along the view of arrow III direction among Figure 44;

Figure 46 be among Figure 44 along the regulating ring view of arrow IV, it rests on the clutch mechanism of friction clutch;

Figure 47 is the sectional view of V-V along the line among Figure 46;

Figure 48 is applied to the view of the opposed regulating ring of clutch pack among Figure 43 along arrow III among Figure 44;

Figure 49 is the sectional view of VII-VII along the line among Figure 48;

Figure 50 is the device of balanced protection shown in a Figure 44 flexible program detail drawing;

Figure 51 is another concrete conceptual view of clutch pack of the present invention;

Figure 52 and Figure 53 are the wear adjustment rings, and it can for example be applied in the clutch pack of the present invention that Figure 51 shows;

Figure 54 A is a sectional view by clutch pack of the present invention;

Figure 54 B is a circular arc sector of the sensor spring used in Figure 54 A;

Figure 55 is the partial view along arrow XIII direction among Figure 54 A;

Figure 56 is another organization plan of friction clutch of the present invention;

Figure 57 is the clutch system sketch of clutch pack of the present invention;

Figure 58 is another organization plan of friction clutch of the present invention, and it has a stopping brake that is used for regulating ring;

Figure 59 is a partial cross section figure by friction clutch of the present invention;

Figure 60 is a partial cross section view of pressing arrow II-II among Figure 59;

Figure 61 is along the sectional view of arrow III-III among Figure 60;

Figure 62 A to Figure 66 A is the different phase of friction clutch operation, and it shows the function that single member and formation are regulated the member of protective gear;

Figure 62 B to Figure 66 B shows the wear compensation ring of regulating protective gear and wear sensor ring corresponding position in Figure 62 A to 66A;

Figure 67 and Figure 68 are respectively another organization plans of friction clutch of the present invention;

Figure 69 to Figure 71 is the another organization plan of friction clutch of the present invention;

Figure 72 and Figure 73 are respectively friction clutch supplementing structure schemes;

Figure 74 and Figure 75 are organization plans of wear sensor of the present invention;

Figure 76 and Figure 77 are the diagrams of different qualities line, therefrom can obtain the single spring element of friction clutch of the present invention and the synergy of regulating element;

Figure 78 is the organization plan of a wear sensor ring, and it is again the structure setting of wear sensor simultaneously;

Figure 79 and Figure 80 are supplementing structure schemes of friction clutch of the present invention;

Figure 81 is a clutch pack sectional view that is provided with according to structure of the present invention;

Figure 82 is a partial view of pressing arrow II among Figure 81;

Figure 83 is one and gives first mounted component unit in order to use the friction clutch shown in Figure 81;

Figure 84 to Figure 86 is the diagram of different qualities curve, therefrom can obtain single spring element and the regulating element and the synergy of clutch pack of the present invention;

Figure 87 is a variant embodiment sectional view according to the friction clutch of structure setting of the present invention;

Figure 88 to Figure 88 C is the other structure plan of establishment of friction clutch of the present invention;

Figure 89 is the diagram of different qualities curve, therefrom can obtain the single spring element of friction clutch among Figure 88 A and the synergy of regulating element;

Figure 90 is the additional structure plan of establishment of of friction clutch of the present invention;

Figure 91 to Figure 93 is a constructional variant scheme of friction clutch of the present invention; Wherein, Figure 92 represents the regulating ring unfolded drawing along the circumferential direction used among Figure 91, and Figure 93 represents along the sectional view of Figure 92 center line XIII-XIII;

Figure 94 represents the diagram of different spring-characteristic lines;

The friction clutch of in Fig. 1 and Fig. 2, describing 1 have a housing 2 with one with this housing do antitorque be connected but axially can make limited mobile platen.Dish spring 4 is pushed in one of tensioning between platen 3 and housing 2 vertically, it can rotate around an annular pivoting support 5 by housing 2 supportings, and this platen 3 can apply effect towards the direction of (fixedlying connected with housing 2 with a bolt 6a) opposed pressing plate 6, for example pressing plate 6 is a flywheel, according to this, the friction pad 7 of clutch disk 8 just is clamped between the friction surface and opposed pressing plate 6 of platen 3.

This platen 3 be the sheet spring 9 that points to by circumferencial direction or tangent line and with 2 one-tenth antitorque connections of housing.Under the present embodiment situation, this clutch disk 8 has so-called pad spring sector 10, it can guarantee a progressive transmission of torque (Drehmomentaufbau) under friction clutch 1 joint situation, simultaneously, these pad spring sectors 10, can make to act on that axial force realizes a progressive raising on the friction pad 7 in limited the moving axially of opposite direction by two friction pads 7.But also can use a clutch disk, wherein, in fact friction pad 7 axially is being that rigidity is placed on the supporting disk.In this case, can use one " pad spring assembly ", that is dish spring series elastic component, for example one between housing and flywheel, or between the part of housing and case side, and elastic component between dish spring and the pressing plate or the elastic component that forms by housing elasticity.

Under the present embodiment situation, dish spring 4 has an annular matrix 4a that can apply extruding force, radially extends into operation tongue 4b thus inwards.This dish spring 4 is structure settings like this simultaneously, that is, the zone that these dish spring 4 usefulness radially outwards are provided with continuously applies and acts on the platen 3, and rotates around pivoting support 5 with the zone that radially is provided with continuously inwards.

This pivoting support 5 comprises two revolution parts 11,12, and they are made of wire rings herein, and axially keeps between them or clamping dish spring 4.Prop up part 11 at dish spring 4 facing to the revolution of a side setting of platen 3, apply with active force along axial direction towards housing 2 by a power storage member 13.This power storage member 13 is to constitute by a dish spring or by the member 13 of a dish spring shape, its fringe region 13a with the outside is bearing on the housing 2 and will turns round a part 11 with the part that radially is provided with continuously inwards and push up on the operation dish spring 4, therefore, also be that axial direction towards housing 2 applies effect.The fringe region 13b that the dish spring 13 that is provided with between platen 3 and operation dish spring 4 has an outside annular radially extends into tongue 13c inward from inner edges, and it is bearing on the revolution part 11.

In order to support the member 13 of dish spring shape, under the present embodiment situation, on housing 2, fixed additional device 14, it constitutes a revolution that is used for dish spring shape member 13 and props up part.These additional devices can be made of each outer fan-shaped member 14 fixing or riveted joint, and each member 14 can be evenly distributed on the circumference.But this device 14 can also be made of the closed member of a ring own.In addition, this bearing device 14 can directly be formed by housing 2 distortion, for example form by the punching out carried out in the axial region of housing 2 or the otch by ligulate, these pressing products or otch the member 13 of dish spring shape embed and tensioning after and in the outer edge zone may of this member 13 owing to material deformation is extruded.In addition, between the member 13 of bearing device 14 and dish spring shape, can also settle the link or the door bolt part of a bayonet formula, in order that the member 13 of this dish spring shape at first can be mended and give tensioning, then it radially can pass through bearing device 14 in the zone of outside in the axial direction.After this, do suitable rotating by the member 13 that makes dish spring shape relative to housing 2, the support region of this member 13 just can be by putting on bearing device 14.Simultaneously, the support region of the member 13 of dish spring shape can constitute by the carriage that radially outward on annular matrix 13b stretches out.

For make operation dish spring 4 rotate safety and in case of necessity the member 13 of dish spring shape rotate safety and, on housing 2, be fixed with axially extended centralising device for making the arrangement of metal ring 11,12 centerings, it is the structure of rivet element 15.This rivet element 15 always has an axially extended nail post 15a, it extends axially by an otch that is provided with between adjacent dish languid 4b, and its regional 13a that can (be shaped on the tongue 13c of the dish spring 13 of corresponding setting with it) partly surrounds.

The member of this dish spring shape or dish spring 13 are structures of sensor spring, and it gives at one and produces a basic at least approximate constant power on the fixed working stroke.By this sensor spring 13, the clutch separation power that applies on the tip of the tongue 4c can be supported, and is at least always setting up an approximate balance in the active force that produces on the revolution part 11 with by sensor dish spring 13 by Separating force between the reaction force that applies on this revolution part 11 simultaneously.Be interpreted as an active force about Separating force, it during actuating friction clutch 1, the tip of the tongue 4c that is applied to the dish languid go up or its release lever on and according to this with sensor spring 13 relativities.

The revolution of case side is propped up part 12 and is bearing on the housing 2 by an adjusting protective gear 16, and this protective gear 16 is arranged in the axial space between dish spring 4 and the housing 2.This adjusting protective gear can be guaranteed, does under the axially displaced situation towards the direction of platen 3 or towards the direction of opposed pressing plate 6 at a revolution part 11 and 12, props up between part 12 and the housing 2 or turning round between a part 12 and the dish spring 4 in revolution can not produce undesirable gap.Just can guarantee thus, when actuating friction clutch 1, not produce undesirable dead stroke or idle stroke.The efficient an of the best just is provided according to this and and then realizes a unquestionable friction clutch operation.The friction surface that occurs in platen 3 and opposed pressing plate 6 and friction pad 7 that moves axially that part 11 and 12 are propped up in this revolution has under the situation of axial wearing and tearing.But in according to device of the present invention, this adjusting also occurs in a revolution part 11, under the situation of 12 wearing and tearing, and occur in the dish spring and axially go up and above-mentioned part 11, under the situation of 12 opposed regions wear, also occur under the dish spring abrasion condition that is positioned at platen supporting convex scope (at the 3a place), in other words on the dish spring with the opposed regions wear situation of this projection under.These pivoting support 5 self-regulating modes of action also will be done to explain in detail in conjunction with the curve diagram of Fig. 8 to Figure 11.

Regulate protective gear 16 and comprise that one applies the regulating element of effect by spring, it be the structure of annular member 17, and is depicted among Fig. 3 and Fig. 4.This annular member 17 have along the circumferential direction extend and at the rising sloping platform 18 that axially increases, it is distributed on the circumference of member 17.Regulating element 17 is so to settle in clutch 1, and the sloping platform 18 that promptly rises is facing to housing bottom 2a.Settle the revolution that is made of wire rings to prop up part 12 on the side of rising sloping platform 18 and deviate from regulating element 17, it centrally is positioned in the setting piece 19 of a flute profile (Fig. 2).Simultaneously, setting piece 19 is structure like this settings, that is, a revolution part 12 in axial direction also is safe and reliable on regulating element 17.This point for example can realize by following measure, that is, on regulating element 17 with setting piece 19 adjacent areas be fixedly clamped at least in part this revolution part 12 or constitute one with turn round the kayser that props up part 12 and be connected.Use under the situation of different materials at a revolution part 12 and regulating element 17, in order to require to compensate according to purpose for the extension difference that when temperature variation is big, produces, at this moment, it is openings that part 12 is propped up in the revolution that makes wire rings, that is on circumference, disconnect in a certain position at least, according to this, wire rings 12 relative capacity spares 19 are along the circumferential direction moved, and therefore make wire rings 12 be adapted to the vary in diameter of setting piece 19.

Under the present embodiment situation, regulating element 17 is made of plastics, and is for example made by a kind of heat-resisting thermoplastic, and it can also additionally carry out fibre strengthening and handle.According to this, this regulating element 17 with regard to available simple mode as the die castings manufacturing.Regulating element by the plastic production of less proportion as carrying, can obtain a less inertia weight, therefore, the receptance of pressure surge has also just been reduced.This revolution part also can directly constitute with plastic hoop.But this regulating element 17 can also be made into panel-like member or make with sintering.In addition, suitably selecting under the situation of material, a revolution part 12 can be provided with the all-in-one-piece structure with regulating element 17.A revolution part 11 can directly constitute by sensor spring 13.Herein, the tip of tongue 13c can have corresponding punching structure or distressed structure, for example crimping (Sicken).

Regulating ring 17 is that the axially extended regional 15a by equally distributed rivet 15 on circumference comes the centering room.For this reason, regulating ring 17 has centering profile 20, and it is made of the perforate 21 of extending at circumferencial direction, and it is positioned at the inside of a revolution part 11 diametrically.In order to constitute perforate 21, this regulating ring 17 is provided with the projection 22 of radially extending inwards in zone, the inside, is positioned at the profile of the perforate 21 of the inside on it defines radially.

As shown in Figure 3, along the circumferential direction observe, between equally distributed perforate 21, respectively be provided with 5 rising sloping platforms 18.And perforate 21 is structure setting like this in a circumferential direction, be that they can allow regulating ring 17 to rotate an angle relative to housing 2 at least, so that this corner is guaranteed the whole length of life at friction clutch 1, when wearing and tearing occurring on the friction surface of platen 3 and opposed pressing plate 6 and on the friction pad 7, when clutch itself weares and teares where necessary, that is for example prop up part 11,12 wearing and tearing, the wearing and tearing of the dish spring part between a part, the wearing and tearing of platen projection (at the 3a place), perhaps on the dish spring 4 with the opposed zone of this projection on wearing and tearing carry out an adjusting when occurring.This regulates the order of magnitude that the angle can be positioned at 8 to 60 degree according to the layout of rising sloping platform, is preferably in the order of magnitude of 10 to 30 degree.Under the present embodiment situation, this corner is in the scope of 12 degree.Simultaneously, the angle of climb 23 of rising sloping platform 18 is positioned at the scope of 12 degree equally.This angle 23 is so to select, that is, the rubbing action that produced under mutual extrusion situation together of the opposed rising sloping platform 24 of the rising sloping platform 18 of regulating ring 17 and the supporting ring 25 described in Fig. 5 and Fig. 6 should be able to prevent to slide between rising sloping platform 18 and 24.According to the material pairing in rising sloping platform 18 and opposed rising sloping platform 24 zones, this angle 23 can be positioned at the scope of 4 to 20 degree.

Regulating ring 17 is along the circumferential direction by spring-loading, and be along regulating direction, that is with this direction loading, be that it can have axial moving towards the direction of platen 3 owing to the rising of sloping platform 18 on the opposed sloping platform 24 of supporting ring 25 causes regulating ring 17, this just means, in axial direction away from radially housing parts 2a.In the embodiment that Fig. 1 and 2 describes, it is to provide by at least one annular dish spring 26 that the elasticity of regulating ring 17 loads, this dish spring for example can have two bung flanges, and on an one termination, has a leg 27 that radially extends, and this leg 27 is to link to each other with regulating ring 17 antitorquely, simultaneously, its other end has an axially extended leg 28, and leg 28 is to be hung on the housing 2 antitorquely.This spring 26 be elastic tension insert.

At the supporting ring 25 shown in Fig. 5 and 6 is to constitute with the member of an annular equally, it has rising sloping platform 24, it constitutes the surface that becomes complementation with the surface that is limited by rising sloping platform 18, simultaneously, can also be consistent by rising sloping platform 18 with the surface that opposed rising sloping platform 24 is limited.The angle of climb 29 of this opposed rising sloping platform 24 is consistent with the angle of climb 23 of rising sloping platform 18.By comparison diagram 3 and 5 as can be seen, rising sloping platform 18 and opposed rising sloping platform 24 along the circumferential direction are similar distributions.Supporting ring 25 is done to be connected with housing 2 antitorquely.For this reason, supporting ring 25 is equipped with the perforate 30 that distributes on circumference, and the prominent head of the riveted joint of rivet 15 can pass perforate 30.

In Fig. 2, dotted another annular dish spring 26a, it and dish spring 26 are similar, can be bent at its end regions, so that guarantee on the one hand and housing 2, realize antitorque being connected with regulating element 17 on the other hand.This spring 26a is that elastic tension is inserted equally, in order that make it apply a warping force on regulating element 17.For some application, use two dish springs 26,26a is favourable, because under friction clutch 1 rotation situation, Qu Yu acts on the reinforcement that centrifugal force on dish spring 26 or the 26a can cause a spring force.By using two dish springs, for example just can be so that the power that occurs on spring 26 increases the power that applies by dish spring 26a and offset.For this reason, dish spring 26 and 26a so reel, and promptly they all should produce active force at centrifugal action under the situation of regulating element 17, and these active forces along the circumferential direction are mutually opposed effects.These two dish springs 26,26a can have one or more bung flanges, in addition, these dish springs 26,26a can have different pitch of the laps diameters, as described at Fig. 2, simultaneously, that link to each other therewith in normal way and act on spring 26, the centrifugal force on the 26a, (it will produce different big or small circumference active forces on regulating element 17), then can be by each spring 26 of suitable configuration, the wire rugosity of 26a and/or pitch of the laps number and obtain balance at least approx.In Fig. 2, spring 26 is footpath the insides of upwards being placed in high joint element 17, and spring 26a is the outside that radially is placed in this regulating element 17.But these two springs also can all radially be placed in the inside or the outside of regulating element 17 by suitably disposing.

Described the plan view of dish spring 26 in Fig. 7 A, at the relaxed state of dish spring 26, leg 27 and 28 is the angles 31 that misplace, and this angle can be positioned at the orders of magnitude of 40 to 120 degree.Under the present embodiment situation, this angle 31 is orders of magnitude of 85 degree.With 32 relative positions of representing leg 27 relative legs 28, its position when in friction clutch 1, using new friction pad 7.Represent the relevant position of leg 27 when friction pad 7 reaches maximum permission wearing and tearing with 33.This regulates angle 34, on the order of magnitude that is in 12 degree under the present embodiment situation.This spring 26 is structure like this settings,, only arranges a metal wire ring 35 when spring 26 relaxes between two legs 27 and 28 that is.Be built-in with the metal wire ring of two axial overlaps at remaining circumferential area.This spring 26a is the structure similar to spring 26, but has a bigger roll diameter and another tension direction when comparing with regulating element 17 shown in Figure 2.Yet being applied to active force on the regulating element 17 by spring 26 is greater than the power that is applied by spring 26a.

When friction clutch 1 is new, the axial projections 18a and the 24a of rising sloping platform 18 and opposed rising sloping platform 24, mutually the most closely (weitesten) axially tightens, and this just means, needs minimum axial arrangement space by the ring of putting 17 and 25 mutually.

In the embodiment shown in Fig. 1 and 2, opposed rising sloping platform 24 or projection (addition) 24a that constitutes the projecture shape of this sloping platform form by self member.Yet this opposed rising sloping platform 24 also can directly constitute with housing 2, for example becomes the projection (addition) of projecture shape by punching out, and it can extend in the shell chamber.This punching out mode is particularly advantageous when the housing of the one of plate shape or housing.

For regulating ring 17 was remained on its position that is pulled before friction clutch 1 assembling, this ring has holding part 36 in the zone of projection 22, and it is used to stop slewing gear or check device, and the check device another side can be bearing on the housing 2.The check device of this form can made or be provided with during assembling friction clutch 1, and is removed be assembled on the flywheel 6 of clutch when friction clutch 1 after, and thus, controlling device 16 is just in running order.Under the present embodiment situation, in housing or housing 2, be provided with the microscler perforate 37 of along the circumferential direction arranging for this reason and a groove or breach 38 are set in regulating ring 17.Simultaneously,, must have an extension part at least, so that make regulating ring 17 can turn round a corresponding to angle in wear adjustment angle with maximum possible in the microscler perforate 37 of circumferential directions.Can also be after friction clutch 1 assembling, axially the fluting 37 by housing imports a turning tool, and snap on the groove 38 of regulating ring 17 or in.After this, this ring 17 can turn round by this instrument, and like this, ring 17 just can move towards the direction of the radial zone 2a of housing 2, and this regional 2a has its minimum axial spacing relatively.Then on this position, make regulating ring 17 location, for example by a clamp or a pin, it snaps in the groove of an aligning of housing and regulating ring 17, rotates to prevent these two members.This pin can be removed from groove after friction clutch 1 is assembled on the flywheel 6, and like this, as already mentioned, this controlling device 16 just has been released.Fluting 37 on the housing 2 is structures so, that is, and and at friction clutch 1 during from flywheel 6 dismountings or after the dismounting, this regulating ring 17 can be placed on its position that retracts.For this reason, clutch 1 is at first drawn back, in order that provide dish spring 4 not apply axial force on a revolution part 12, and therefore, guarantees that regulating ring 17 can carry out no problem ground and rotate.

An other possible scheme is, the member that is fixed to the friction clutch 1 on the internal-combustion engine is placed on the position that it is suitable that is worked, that is, with regulating element or regulating ring 17, be assembled on the internal-combustion engine or just turning round or adjust back later on its flywheel.For this reason, for example can come actuating friction clutch 1 by an assistant tool, then, in fact unloaded ring 17 is adjusted on the position that its relative pressing plate pulls back.Then, this friction clutch 1 is engaged again, in order that encircle 17 positions that at first keep this to pull back.

This annular regulating element 17 or supporting ring 25 can also always have two groups in radial misalignments, extend at circumferencial direction and at the rising sloping platform that axially increases, they are distributed on the circumference of this member separately.Simultaneously, the rising sloping platform of settling outside this rising sloping platform that directly makes progress the inside can relatively directly make progress along the circumferential direction misplaces, and, the length of the length of about half sloping platform that misplaces or half sloping platform spacing.By just guaranteeing, between regulating ring 17 and supporting ring 25, realize the centering leading of a no problem at the sloping platform of circumferencial direction dislocation.

Now, in conjunction with the characteristic curve sketch of record among Fig. 8 to 11, describe the working method of aforementioned friction clutch 1 in detail.

Curve 40 among Fig. 8 has shown that the tapering owing to dish spring 4 changes the axial force that produces, and dish spring 4 axial force under the distortion situation between two supporting tongues, and the radial spacing between the supporting tongue and pivoting support 5 and the footpath radial spacing that is bearing between the diameter 3a on the platen 3 outside upwards is consistent.Two strokes to axial between part are being described on the abscissa; State the active force that produces by the dish spring and on y coordinate, insert.This point 41 is represented the design attitude of dish spring, it is the rigging position of dish spring 4 selected under the situation of closed clutch 1 that this position requires according to purpose, that is when this position, dish spring 4 is applied to the extruding force of maximum on the platen 3 for this corresponding rigging position.This point 41 can be by changing the rigging position of taper, that is change the setting of dish spring 4 and move downwards or down along curve 40.

Curve 42 has been described the power of axially opening that is applied by packing spring sector 10, and it acts between two friction pads 7.It is opposite with the responsive to axial force that is applied on the platen 3 by dish spring 4 that this axially opens power.Favourable mode is, the essential axial force of resiliently deformable is consistent with the power that is applied on the platen 3 by dish spring 4 at least as far as possible in order to make spring sector 10.Under friction clutch 1 separation case, spring sector 10 is just lax, and through stroke 43.The corresponding to stroke 43 that moves axially by this and platen 3, separation process to clutch 1 is favourable, this just means, need only apply a less maximum separation power, that is the maximum separation power corresponding to assembling point 41 is little when not filling up spring sector 10 (not filling up elastic component).Surmounting a little under 44 the situation, this friction pad 7 is released, simultaneously because the characteristic curve zone decrescence of dish spring 4, also the Separating force that will apply just than with put 41 corresponding Separating forces and obviously reduced.The Separating force that is used for clutch 1 all reduced before arriving minimum value or valley point 45 along sinusoidal curve 40.When surpassing minimum value 45, essential Separating force just rises again, simultaneously, separation stroke in the lip of the tongue 4c scope is so to select, that is, even surpassing under minimum value 45 situations, Separating force also is no more than the maximum separation power of determining at point 44, preferably keeps below this Separating force.That is should not surpass point 46.

Spring 13 as force transducer has a stroke-force curve, and it is corresponding with the curve 47 among Fig. 9.This characteristic curve 47 is corresponding from the power that lax position change produces when it has tapering with the member 13 of dish spring shape, and occur between two pivoting supports, these two pivoting supports have a radial spacing, and it is consistent with the radial spacing between the revolution part 11 and 14.Show that as characteristic curve 47 member 13 of this dish spring shape has a spring travel 48, in this stroke, in fact keep constant by the axial force of its generation.Simultaneously, the active force that produces in this zone 48 is so selected, that is, this power is approximate consistent with the clutch separation power that Fig. 8 mid point 44 places determine at least.The supporting force that is applied by sensor spring 13 is compared corresponding to the power of point 44 with dish spring 4, is that the lever ratio according to this dish spring 4 reduces.This transmits ratio, in most of the cases, is positioned at the order of magnitude between 1: 3 to 1: 5, but can also be big slightly or slightly smaller for some application.

The dish spring transmission of having mentioned is than consistent to the ratio between (for example for a disengaging configuration) radial spacing that diameter 4c is installed to radial spacing and the pivoting support 5 of supporting tongue 3a with pivoting support 5.

The element 13 of dish spring shape is so selected at the rigging position of friction clutch 1, promptly, this element 13 can move an axial spring travel towards the direction of friction pad 7 in the scope of pivoting support 5, this spring travel is not only consistent towards the axial adjustment stroke of opposed pressing plate 6 directions with platen 3 at least, (this adjustment stroke is owing to the wearing and tearing of friction surface and friction pad produce), and also should guarantee an approximate at least constant axially mounting power for pivoting support 5.This means that the linearity region 48 of characteristic curve 47 should have certain length, it is consistent with the wearing and tearing stroke of mentioning, preferably greater than this wearing and tearing stroke, because like this, build-up tolerance can partly be compensated at least.

In order when friction clutch 1 separates, to make friction pad 7 obtain a point of release 44 stable or that limit, can between friction pad 7, use a so-called biparting shape pad spring, that is, the pad spring that each spring sector is provided with in back-to-back and paired mode, simultaneously, each sector is axially gone up the mutual tensioning of giving substantially to having one, in order that, make the whole axial force that applies by the pad spring, under the not clamped situation of clutch disk 8, at least consistent, preferably higher slightly with dish spring 4 corresponding to the Separating force of point 44.Give tensioning by filling up the spring assembly that is provided with between part, can realize that the loss of the intrusion pad spare dorsal part that sector occurs is compensated or offsets at least substantially between on-stream period.

So-called intrusion loss is interpreted as such loss, and it is to invade the dorsal part that fills up part by sector to produce.According to the purpose requirement, the giving tensioning and should be in the order of magnitude of 0.3mm to 0.8mm of the spring assembly that is provided with between part at pad is preferably on the order of magnitude of 0.5mm.By the axial elasticity stroke between two friction pads 7 being done a suitable restriction and by the spring assembly that acts on is done the tensioning of giving of a qualification between friction pad, also can realize, at least when friction clutch 1 separated, platen 3 was squeezed back the stroke 43 of a qualification by the spring assembly that is provided with between the pad part.Be the stroke 43 of realizing a qualification, can pass through corresponding bounding means, make not only in the lax direction of pad spring 10 but also can both between friction pad, limit axial stroke on the tension direction.As the pad spring assembly, those are known, as long as related to the present invention can being applied with optimal way, for example the pad spring among the P4206880.0 just can be applied in the present techniques scheme significantly.

In Figure 10, curve 49 expression with one the resolution element of the 4c zone installation of dish spring for make clutch separation with platen from putting 41 necessary active forces when moving to a little 44 (Fig. 8).In addition, curve 49 is also represented the stroke of dish spring at the lip of the tongue in 4c zone.

In order to ensure friction clutch 1 perfect performance is arranged, perhaps best performance is arranged in order to ensure the controlling device that the wearing and tearing of pad part can be compensated automatically, importantly (observe) from the Separating force curve that in fact occurs 49 shown in Figure 10, at first by pad spring 10 and sensor spring 13 apply on the dish spring 4 with the active force that increases should be greater than the active force that is applied to by dish spring 4 on the part 11.Also have, after platen 3 is thrown off from friction pad 7, still by sensor spring 13 be applied on the dish spring 4 active force should greater than should equal at least to apply in dish languid point 4c zone with according to Figure 10 by separating the necessary separation force (according to curve 49) with variation of stroke.Simultaneously, the active force that is applied on the part 11 by sensor dish spring 13 should so limit in addition, to prevent that promptly ring 17 under the power effect of spring 26 from rotating and prevent the dish spring because of moving axially that rotation causes, at least near to but be no more than point of branching 41 corresponding on the curve 40 with dish spring rigging position.

What consider so far is that dish spring 4 has a completely specified rigging position, and thinks there are not wearing and tearing on friction pad 7.

Under the abrasion condition of axial wearing and tearing, for example friction pad 7, just move towards the direction of opposed pressing plate 6 position of platen 3, thus, the tapering of dish spring just changes (from the observer, the tip of the tongue 4c drifts about to the right), like this, also change by the extruding force that the dish spring applies, and change towards increasing direction at the jointing state of friction clutch 1.This variation then causes, point 41 is towards the drift of point 41 ' direction and put 44 and move towards point 44 ' direction.Because this variation, when making that clutch 1 is thrown off between operation dish spring 4 and the sensor spring 13 on revolution part 11 zone equilibrium of forces of original existence destroyed.Because the dish spring that the wearing and tearing of pad part cause also causes the Separating force curve towards the displacement that increases direction to the raising of these platen 3 squeezing action power.Consequent Separating force curve is with dashed lines 50 expressions in Figure 10.Because the height of Separating force curve moves, during the separation process of friction clutch 1, the axial force that is applied on the dish spring 4 by sensor spring 13 just has been overcome, so that sensor spring 13 produces an axial stroke in the zone of pivoting support 5 distortion, this stroke is consistent with the wearing and tearing of friction pad 7 basically.In the elastic stage of this sensor spring 13, dish spring 4 is bearing on the Shi Zai district 3a of platen 3, therefore, dish spring 4 has changed its tapering, and therefore, in this dish spring 4 energy stored or the torque that stores therein and and then by dish spring 4 on a revolution part 11 or on the sensor spring 13 and the active force that applies on the platen 3 all to change.This variation as shown in Figure 8, is to be applied to the direction that the active force on the platen 3 reduces along dish spring 4 to carry out.This variation exists always, has only when dish spring 4 props up in revolution just to stop when the axial force that is applied on part 11 zones on the sensor spring 13 balances each other with the reaction force that is produced by sensor spring 13.This just means, in the curve of Fig. 8, and point 41 ' and 44 ' again direction drifts towards point 41 and 44.After this balance formed again, platen 3 just can leave from friction pad 7 again.During this wear adjustment stage, that is in the separation process of friction clutch 1 between sensor spring 13 deformation phases, the regulating element 17 of controlling device 16 is to rotate by giving tight spring 26, according to this, a revolution part 12 is the drift thereupon according to the wearing and tearing of pad part also, and therefore can guarantee 4 one gapless pivoting supports 5 of dish spring again.After this adjustment process, the Separating force curve is consistent with curve 49 among Figure 10 again.Curve 50 and 51 among Figure 10 has been represented the axial stroke of platen 3 when a Separating force corresponding with curve 49,50-stroke curve.

Described the change curve of power relative separation stroke in curve shown in Figure 11, this separates stroke and is applied to power on the housing 2 in separation process or on the dish spring 13 and produce, maximum value is clipped here.A power at first begins to affact on the housing 2 from engagement positio shown in Figure 1, therefore also just affacts on the platen 3, and this power is corresponding with the mounting points 41 (Fig. 8) of dish spring 4.In separation process, be applied on the housing 2 or the axial force of a revolution part 12 reduces according to the line among Figure 11 52 by dish spring 4, and be reduced to a little 53 always.When surpassing point 53 at detaching direction, at dish spring axial restraint but be bearing in pivotally on the housing 2 in the common clutch of (that is a revolution part 11 axially is not connected with housing 2 to deflection), then affact the power of an axial opposed on the radial height that is positioned at pivoting support 5 of housing 2 by dish spring 4.In according to clutch of the present invention, in the zone of pivoting support 5, this opposite shaft orientation power that produces in the zone of pivoting support 5 by dish spring 4 is then born by sensor spring 13.Dish spring 4 leaves the Shi Zai district 3a of platen 3 when the point of arrival 54.At least before point 54, the separation process of friction clutch 1 is by the axial force support that applies from pad spring 10, because this axial force is being resisted disc spring force.Simultaneously, this separates the increase of stroke from the power of pad spring 10 along with the lip of the tongue 4c or reduces along with the increase of the axial separation stroke of platen 3.Curve 52 has also represented to act on the one hand the Separating force of the lip of the tongue 4c and the making a concerted effort of axial force that is applied to dish spring 4 on the other hand at radial zone 3a by sheet spring 10 in separation process.When surpassing point 54 at detaching direction, dish spring 4 is applied to the opposite force supporting of the axial force origin autobiography sensor dish spring 13 on the revolution part 11, simultaneously, these two power are balances after platen 3 is with friction pad 7 off-loads at least, and preferably are slightly larger than predetermined Separating force by sensor spring 13 in the axial force that the zone of pivoting support 5 produces in the continuity section of separation process.Part area 55 demonstrations of characteristic curve 52 shown in Figure 11: be applied to the power of turning round on the part 11 along with the increase Separating force that separates stroke or by dish spring 4 and diminish with respect to the Separating forces of being scheduled at point 54.Dotted line 56 is corresponding with a kind of state of friction clutch, wearing and tearing occur in the zone of friction pad 7 in this state, but also regulates in the zone of pivoting support 5.Here also show: the change of the rigging position of the dish spring 4 that causes by wearing and tearing make act on the housing 2 and a revolution part 11 on or on the sensor spring 13 power increase.This especially causes such consequence: point 54 is to the drift of point 54 ' direction, like this, in the separation process again of friction clutch 1, be applied to axial force on the sensor spring 13 in the zone of revolution part 11 greater than the reaction force of sensor spring 13, the therefore adjustment process of having narrated by the axial deformation of sensor spring 13 by dish spring 4.By adjustment process by spring 26 effects, that is by the rotation of ring 17 and the axial displacement of a part 12, point 54 ' again moves to point 54 directions, therefore, props up the zone of part 5 and set up desirable state of equilibrium again between dish spring 4 and sensor spring 13 in revolution.

In fact apart from carrying out, institute thinks understands the present invention preferably continuously or with small step very in described adjusting, and the big displacement of point of drawing in the drawings and characteristic line does not occur usually.

Several running parameters or operation point may change between the on-stream period of friction clutch 1.For example, because improper actuating friction clutch may cause the overheated of pad spring 10, may make that pad spring or 10 depressions of pad spring sector are that axial elastic force reduces.But the curve 47 of characteristic line 40 by dish spring 4 is set suitably and corresponding adjustment sensor spring 13 just can guarantee the service behaviour of friction clutch.The axial edge of pad spring 10 falls into and may only cause such result, promptly occupies a position of more stretching with respect to position dish spring 4 shown in Figure 1, and is therefore smaller by the impacting force that dish spring 4 is applied on the platen, from curve shown in Figure 8 40 as seen.And then sensor spring 13 produces corresponding axial deformation and a revolution part 11 produces corresponding axial displacement.

According to another inventive concept, total the supporting force that acts on the dish spring 4 can improve with the increase of the wearing and tearing of friction pad 7.And this raising can be limited at the total maximums of friction pad 7 and allows in the section of wearing and tearing stroke.Simultaneously, the raising to the supporting force of operation dish spring 4 can realize by sensor spring 13 is set suitably.In Fig. 9, represent an individual features curve by zone 48 with label 47a and dotted line.The supporting force that improves operation dish spring 4 along with the increase of wearing and tearing can make the reduction of the impacting force of 4 pairs of platens 3 of operation dish spring be compensated at least in part, and the reduction of impacting force is owing to pad spring elasticity reduces to produce, for example in the sector intrusion pad part.The supporting force of operation dish spring 4 being improved invade in the pad part with pad spring depression or sector is particularly advantageous when proportional.This means that along with thick reducing coiled in pad part zone, just invade and/or fill up spring because of sector and along falling into and/or fill up the part wearing and tearing distance between the friction surface that fills up part is reduced, the supporting force of being mentioned should improve.Simultaneously, it is particularly advantageous that supporting force improves like this, promptly improves in the power of the first section internal ratio in back to back second section and wants big, and these two sections all are positioned at section 48 as shown in Figure 9.The latter's setting is favourable.Because the spring sector of having mentioned is invaded part with the maximum of pad part and mainly occurred in friction clutch in very little a period of time of entire life, the ratio of this rear spring sector and friction pad spare is stable on realizing.This means that since a definite intrusion, intrusion just no longer includes substantially and changed.The supporting of operation dish spring improves in can also be during the wearing and tearing of at least a portion friction pad.

In the adjustment process of aforesaid friction compensation pad wearing and tearing, consider the axial force that may apply by sheet spring 9.With regard to platen 3 is removed from corresponding friction pad 7 or with regard to the extruding of 3 pairs of dish springs 4 of platen, when sheet spring 9 gives tensioning, just separation process is formed and support.Power and Separating force that axial force that is applied by sheet spring 9 and bent sensor spring 13 and dish spring 4 apply are superimposed.In order to understand better, in the description of Fig. 8 to 11, do not consider the axial force that sheet spring 9 applies.Prop up total power that part 12 applies in the revolution of 4 pairs of case side of the separated state of friction clutch 1 operation dish spring and obtain, promptly mainly by sheet spring 9, sensor spring 13 and the power that applies by the Separating force that acts on the operation dish spring 4 by several power additions.Simultaneously, sheet spring spare 9 can be arranged on like this between housing 2 and the platen 3, i.e. increase along with friction pad 7 abrasions becomes big by the axial force that sheet spring 9 is applied on the operation dish spring 4.So, example as shown in FIG. 9 stroke 48 and the between centers power that during the abrasion of controlling device 16 compensation stroke, applies by sheet spring 9 have the tendency of line 47b.Can find out also that from Fig. 9 also increase along with the resilience of sensor spring 13 increases the returning place force that is applied on the platen 3 by sheet spring 9, this readjustment power also affacts on the operation dish spring 4.With the superimposed change curve with joint efforts that obtains of power change curve that characteristic curve 47b and dish spring characteristic curve are represented, its axial action and is propped up the revolution that dish spring 4 is expressed to case side on the part 12 to dish spring 4.In order to obtain change curve 47a (simultaneously, at the beginning of control band 47d initial power being set at first increases, change a constant substantially power zone then over to), then the sensor spring is provided with like this and meets the requirements, and promptly it has the characteristic line that changes corresponding to curve 47c among Fig. 9.By obtaining power change curve according to the power change curve of curve 47c with according to the power change curve addition of curve 47d according to curve 47a.That is also can reduce the supporting force or the supporting force change curve that apply by the sensor spring by suitable pre-tensioned spring 9.Arrange suitably and arrange sheet spring 9 equally can (at least in part) compensation pad spring is flexible reduces and/or fill up the spring sector to filling up the intrusion of part.Can guarantee also that thus dish spring 4 keeps same operation point or same working zone basically, so dish spring 4 interimly applies an extruding force of approximately constant at least to platen 3 basically in friction clutch whole working life.And then when friction clutch is set, when sensor spring 13 and/or sheet spring 9 particularly are set, Regulation spring 26 and/or the axial of 26a generation that must consider to affact on the regulating element 17 are made a concerted effort, and this axially makes a concerted effort reverse with the active force of sensor spring 13 and/or sheet spring 9.When having the friction clutch 1 of pre-tensioned spring 9, setting also must consider, because the pre-tensioning of sheet spring 9 is affected by the axial force that platen 3 is applied on the friction pad 7.This also means, the impacting force that is applied by dish spring 4 under the pre-tensioned situation of direction of operation dish spring 4 at sheet spring 9 just reduces the amount that equates with the pre-tensioning of sheet spring 9.In this friction clutch 1, just form one for platen 3 or for the change curve of total extruding force of friction pad 7, it is by the impacting force change curve of dish spring 4 and the tension force change curve stack of sheet spring 9 are obtained.Suppose that the working area of friction clutch 1 (observe) indicatrix 40 shown in Figure 8 represented by operation dish spring 4 and pre-tensioning sheet spring 9 change curve of making a concerted effort when the friction clutch new state, when dwindling because of the wearing and tearing of pad part along with the distance between platen 3 and the opposed platen 6 so, the change curve of making a concerted effort moves to reducing direction, provided a dotted line 40a in Fig. 8, it is corresponding to the pad spare wearing and tearing total amount of 1.5mm.Because the curve 40 that occurs in the life-span of wearing and tearing clutch moves to curve 40a direction, the axial force that is applied on the sensor spring 13 by dish spring 4 when friction clutch 1 separates then reduces, and based on being applied to countertorque on the dish spring 4 by sheet spring 9 with the wearing and tearing that increase.This moment of reaction is based on pivoting support 5 and execute and carry the radial distance between the diameter 3a and be present between operation dish spring 4 and the platen 3.

When friction clutch 1 is set, making the increase of sheet spring 9 tension forces that produce because of the wearing and tearing of pad part is very important less than the Separating force increase that produces because of identical pad spare wearing and tearing, desired continuous revolution when this Separating force increase makes sensor spring 3 take place to regulate.Otherwise the extruding force at 3 pairs of friction pads 7 of jointing state platen of friction clutch descends, even can not regulate at all.

The friction clutch described in Figure 12 and Figure 13 101 is with the main distinction of friction clutch 1 in Fig. 1 and Fig. 2 describe, regulating ring 117 by helical spring 126 in circumferential loading.With regard to the function and the mode of action of its friction compensation pad wearing and tearing, regulating ring 117 is identical to regulating ring 17 shown in Figure 4 with Fig. 2.Be provided with 3 helical springs 126 in this embodiment, their are along circumferentially uniform and be stretched between clutch housing 2 and the regulating ring 117.

Especially as can be seen from Fig. 14, regulating ring 117 has radial projection or step 127 interior week, make helical spring 126 that arc settles can with the one end bearing on projection 127 with to regulating ring 117 along circumferentially loading.The other end of spring 126 is bearing on the bounding means 128 by clutch housing 2 supportings.In this embodiment, bounding means 128 is made of link similar screw and that be connected with housing 2.Certainly bounding means 128 also can be made of axial drip molding, and it is arranged to clutch housing 2 integrative-structures or equips on it.For example, bounding means 128 can be block that is stamped to form or the baffle plate that axially stretches out from thin walled shell 2.Especially from Figure 13 and 14 as can be seen, ring 117 constituted like this in interior week, promptly at least mainly a guided portion 129 is set, axially support and radial support that guided portion 129 is realized spring 126 in the extension region of spring 126 and in the angle of rotation of adjusting the ring 117 that requires of especially wearing and tearing or on the unloading stroke of spring 126.Spring guided portion 129 is made of semiorbicular (from the cross section) groove roughly in the present embodiment, and its interface cooperates with the cross section of helical spring 126 basically.

Such structure has the following advantages, and promptly can guarantee the leading of spring 126 no problems in the friction clutch of rotation, so spring 126 axially can not depart from.For helical spring 126 is insured more, as shown in figure 13, axial forming section 130 is set in the inner radial fringe area of housing 2, it is axially taking spring 126.Housing 2 also can have one along circumference and axially extended inward flange 130 to substitute single forming section 130.Inward flange 130 can be used for limiting the loose of dish spring 4.

The guiding device of the Regulation spring 126 that Figure 12 is extremely shown in Figure 14 has the following advantages, promptly in the clutch unit 1 of rotation, each circle of spring 126 can radial support under centrifugal action on regulating ring 117, simultaneously, owing between spring ring and regulating ring, have surface friction drag, reduce or be cancelled fully along the adjusting power that circumferentially applies and make by spring 126.When friction clutch 101 rotations (owing to having the frictional force that hinders spring action), in fact spring 126 may be in stiff state.Therefore, can realize that when rotating speed was higher than the idling of IC engine rotating speed, regulating ring 117 was not rotated by spring 126 at least.Therefore, can realize also that during in racing speed or at least near racing speed, only the wearing and tearing of friction pad are just compensated when actuating friction clutch 101.But also locking regulating ring 117 like this when promptly only just friction clutch 101 does not change when internal-combustion engine does not change, carries out the adjusting at the wearing and tearing of pad part.

The locking adjustment process may also be favourable to embodiment illustrated in figures 1 and 2 when friction clutch rotates or when surpassing certain rotating speed.Be arranged under the centrifugal action device that the rotation to regulating element 17 shields on for example can housing 2 to this, and with the adjusting power acting in opposition that produces by belleville spring 26 and/or 26a.Simultaneously, this locking closure can be made of at the pouring weight of radially outward extruding under the centrifugal action at least one, for example this pouring weight can be bearing on ring 17 the inward flange and can produce friction there, this friction causes a braking moment on ring 17, this braking moment is greater than the running torque that is applied to by Regulation spring on the ring 17.

For the extending body of radial support at least a portion spring 126, the bearing device by housing 2 supportings can also be set.This bearing device can constitute with bounding means 128 one in Figure 12 and 13 illustrated embodiments.For a little bounding meanss 128 can be angular structures, so it always has the part at extending circumferentially, this part extends through a part of extending body of spring 126 at least and stretches in this spring 126.Therefore, can be guided and live at radial support at least by at least a portion spring ring.As shown in figure 13, the wire rings 11 that is provided with in Fig. 2 is removed and is substituted by the drip molding 111 that the lip of the tongue at sensor spring 113 is provided with.Make spherical at the cusp field of tongue 113c and a side of its oriented manipulation spring 4 for this reason.

In Figure 15 to 17, described another variant embodiment of compensate for wear of the present invention, in this embodiment, substituted the regulating ring of an annular and use single adjusting element 217.These adjusting elements are along the circumference uniform distribution of housing 202.Adjusting element 127 is made of button shaped or discoidal member, and it has at extending circumferentially and the axial rising sloping platform 128 that rises.The adjusting element 217 of annular has eating dishes without rice or wine of central authorities or through hole 219, passes hole 219 by the part 215a that extends axially of the rod of housing supporting, so adjusting element 217 rotatably is placed on this extension piece 215a.Be provided with punching out part 225 on housing 202, it is configured for the opposed sloping platform 224 of sloping platform 218.Spring part 226 of tensioning between an adjusting element 217 and housing 202, it loads the sense of rotation of adjusting element 217 in redeeming.As seen from Figure 15, spring part 226 can extend around extending axially part 215a, just is approximately helix structure.End regions at spring 226 can be provided with distortion, for example crooked or bending so that with spring one end bearing on housing 202, the other end is bearing on the corresponding adjusting element 217.During in revolution part 205 regional axial displacements, adjusting element 217 is rotated and compensates this displacement by sloping platform 218 in the rising of sloping platform 224 at dish spring 204 or sensor spring 213.

On housing 202, this plate is formed by housing 202 axially extended region deformations sensor spring 213 by fish plate 214 axially mountings, and axially inwardly is squeezed in the perimeter of sensor spring 213.

The adjusting element 217 of annular has following advantage, and its regulating action can be irrelevant with centrifugal force in to a great extent.

The adjusting element 217 that substitutes the rotation described or rotation itself in Figure 15 also can use the adjusting element of single wedge shape, is compensate for wear, and these wedge shape adjusting elements are radially and/or circumferentially be mobile.This wedge shape adjusting element can have a microscler perforate, and for corresponding adjusting element is guided, one extends axially part 215a and can pass this slotted hole.This wedge shape adjusting element can be according to the centrifugal force redeeming of effect thereon.Yet, also the power storage can be set, it is executed at compensation direction the adjusting element of wedge shape and carries.For the wedge shape adjusting element is carried out the guiding of no problem, housing 202 can have shaping.One relative with the plane of arranging perpendicular to the running shaft of friction clutch and can be arranged on case side and/or operating spring side with the adjusting element wedge-shaped surface of certain angle of climb setting.When using the discrete component of this wedge shape, make wedge with light material and meet purpose, so that the centrifugal force that will act on it drops to minimum value.

Material between the member that forms the adjusting sloping platform promptly in the operating life of friction clutch, the bonding of compensation can not occur hindering to preferably selecting like this between rising sloping platform and opposed rising sloping platform.For fear of so bonding, in opposed sloping platform district, sloping platform zone coating is set at least one this member and at least.When using two metal constructions, can avoid corrosion especially by this coating.In addition, constitute to regulate bonding between the member of sloping platform or cementing and to avoid by following measure, promptly supporting is made by the material with different expansion coefficient with the member that constitutes sloping platform and opposed sloping platform mutually, so that because the temperature fluctuation that the friction clutch duration of work occurs makes the surface (constituting the surface of regulating sloping platform) that is in contact condition realize mutual relative movement.According to this, the member of formation rising sloping platform and opposed rising sloping platform often keeps the state of relative movement.That is, between these parts, can not produce bonding or cement, because because different expansions, these parts always disconnect again mutually and separate.Regulate separately also can reaching like this of sloping platform, that is, because parts have different intensity and/or structure, the centrifugal force that affacts on these parts can cause different stretching, extensions or motion, and this stretching, extension or motion have been avoided the adhesion of parts or cemented.

Be connected with adhesion between opposed rising sloping platform for fear of the rising sloping platform, also at least one antisticking device can be set, it applies an axial force to one or more adjusting elements when friction clutch separates or when wear compensation.For this reason, 17,117 and members shaft of adjusting element are to linking together, and this member has some sections, and these sections can move axially when wearing and tearing occurring.This connection especially can produce in the zone of a revolution part 5, and is to be connected with operating spring 4 and/or sensor spring 13.

Described an extruding dish spring characteristic curve 340 in curve shown in Figure 180, this curve has a lowest point point or minimum point 345, in this point by pushing the force rate less (ca.450Nm) that the dish spring applies.Maximum, force with dish spring of stroke-force characteristic curve 340 is positioned at the magnitude of 7600Nm.Characteristic curve 340 by two radially the distortion of the dish spring between the supporting tongue of interbody spacer obtain, and as the same with the description of carrying out about dish spring 4 in conjunction with characteristic curve shown in Figure 8 40.

Dish spring characteristic curve 340 can be combined with a pad spring characteristic curve 342.As shown in figure 18, the stroke-Z-TEK of pad spring sector levy curve 342 be near extruding dish spring indicatrix 340 or two curves only extend with very little spacing, so just can operate corresponding friction clutch with very little power.In the working zone of pad spring, theoretical Separating force is produced by curve 340 and 342 two vertically superposed some differences.Such difference is with label 360 expressions.The actual Separating force that requires reduces by the corresponding lever ratio of operating element (as the dish languid).This described in Fig. 1 and 2 illustrated embodiment and in plotted curve shown in Fig. 8 to 11 equally.

Another operation dish spring characteristic curve 440 is represented by dotted lines in Figure 18, this curve has a minimum point or the lowest point point 445, the power that bent in this dish spring applies is born, and promptly is not to act on the direction of engagement of corresponding friction clutch but act on detaching direction.This means meaning, keeps separately automatically at the separation phase friction clutch surpassing point 461 o'clock.Dish spring characteristic curve 440 can be set up the pad spring characteristic curve of a corresponding curve 442, so that obtain minimum separation power, pad spring characteristic curve 442 should extend with dish spring characteristic curve 440 as far as possible abreast.

Described to be applied to when corresponding friction clutch separates the change curve of the Separating force relative separation stroke on the operate lever (as the dish languid) in Figure 19, this separates the corresponding characteristic curve 340 and 342 or 440 and 442 of stroke.Obviously, Separating force change curve 349 (corresponding characteristic curve 340 and 342) always is in positive power scope, this means, for clutch is remained on separated state, always needs a power at detaching direction.Separating force change curve 449 (corresponding characteristic curve 440 and 442) has a section 449a, and Separating force at first reduces in this zone, turns to negative power scope from positive power scope then, so corresponding friction clutch does not need confining force in separated state.

In the embodiment of the friction clutch shown in Figure 20 A, 20B and 21 501, sensor dish spring 513 axially is bearing on the clutch housing 502 through the connection 514 of a bayonet formula.For this reason, sensor spring 513 has the connecting plate 513d that radially extends from the excircle of the matrix 513b of annular, this plate with the form axially mounting of the connecting plate that stretches out from housing on radial zone 502a.The overhanging formation of axially extended fringe area 502b on the matrix of housing connecting plate 502a by housing meets the requirements when connecting plate 502a is at least in part by an open incision 502c or 502d and at first with the overhanging shaping of housing for this reason.Cut connecting plate 502a by enclosing at least in part, make it can be more yielding at its assigned position.Especially as seen, connecting plate 502a and semi-girder or tongue 513d dispose like this, and promptly sensor spring 513 can relative housing 2 centerings from Figure 21.Connecting plate 502a has an axial small stair 502e in the present embodiment for this reason.

Connect at 514 o'clock in order to guarantee the location of sensor spring 513 relative housing 502 no problems at the pintle hook lock of making the bayonet formula, at least 3 are preferably disposed about other shell area like this along the connecting plate 502a of housing 502 circumference uniform distributions, promptly according to relatively rotating of limiting between sensor 513 and housing 502, corresponding semi-girder 513d will come to a circumferential limit stoper 502f and go up also so avoid further relatively rotating between sensor spring 513 and housing 502.Especially as seen, bounding means 502f is made of the portion of extending axially of housing 502 in the present embodiment from Figure 20 B.Can find out further that from Figure 20 B at least one best three connecting plate 502d forms another rotary spacing spare 502g between the tongue 513d of housing 502 and sensor spring 513.Same connecting plate 502a forms the rotation protective gear 502f and the 502g of two sense of rotation in described example.Avoid the bounding means 502g that throws off at sensor spring 513 and housing 502 by axial, constitute at the crimp of the tongue 502a that radially extends.Provide the location determined of sensor spring 513 relative housings 502 by circumferential bounding means 502f to 502g at circumferencial direction.Connect 514 in order to form pintle hook lock, sensor spring 513, supports on the 502a so that tongue 513d axially embeds among open cuts 502c and the 502d and axially is against housing to tensioning at housing 502 axis of orientations.Then, housing 502 and sensor spring 513 can relatively rotate, and come on the rotary spacing spare 502f up to several tongue 513d.Therefore sensor spring 513 partial relaxations, thus from circumferencial direction see several tongue 513d between corresponding bounding means 502f and the 502g and all tongue 513d be installed on the supporting 502a of case side.Structure by bayonet formula card locking device 514 of the present invention guarantees that tongue 513d can not lean against on the part 502a of case side when assembling friction clutch 1.

In described embodiment so far, annular matrix (for example 513b) footpath that really applies the sensor spring 513 of elastic force is upwards outside Shi Zai district or the supporting area and in platen with operate between the dish spring and be provided with.But in some application, the annular matrix of sensor dish spring directly upwards also meets the requirements executing to carry within the diameter and be provided with between platen and operation dish spring.This also means concerning form of implementation illustrated in figures 1 and 2, and the matrix 13b that sensor spring 13 is applied axial tension force is directly upwards within the Shi Zai district 3a and setting between operation dish spring 4 and platen 3.

In the form of implementation shown in Figure 20 A to 21, the opposed rising sloping platform 524 of case side is made of the drawing part of the cam-shaped of punching out on thin sheet casing 502.In this external this form of implementation, the helical spring 526 of tensioning is by guiding mandrel 528 guiding between housing 502 and regulating ring 517, and guide finger is with regulating ring 517 one formation and at extending circumferentially.Especially as seen, these guide finger 528 axially have a microscler section, and it cooperates with the internal diameter of spring 526 from Figure 21.Guide device 528 enters in this spring 526 by a part of longitudinal extension body of spring 526 at least.Therefore, at least a portion spring ring can be directed to and radially can be supported at least.In addition, spring 526 axially can avoided crooked and eject.By being set, pin 528 also can make the assembling of friction clutch easier.

In Figure 22, drawn the part of regulating ring 517.Regulating ring 517 has the shaping 527 that extends radially inwardly, it be supported be used for helical spring 526 and at the pin shape guiding area 528 of extending circumferentially.In the present embodiment, spring holding area 528 constitutes with plastic hoop 517 one of producing as the spray part.But spring guide portion or spring holding area 528 can be made of together single member or all independent members, and these single or multiple members for example are connected with a bitelock card device with regulating ring.Like this, all guiding areas 528 can constitute at the ring of circumferential openings in case of necessity by one, and it is connected at three link positions at least with regulating ring 517, and preferably the bitelock card device connects.

With Figure 12 and 13 described similar, helical spring 526 (for example because action of centrifugal force) also may radial support on the relative set zone of housing 502 and/or regulating ring 517.

The case side supporting that is used for helical spring 526 be form by the case material cutting and constitute with axially extended fin or by the punching out position 526a that axial walls portion forms.Simultaneously, this supporting area 526a of spring 526 structure like this meets the requirements, and promptly the respective end of spring is directed to protection in the unallowed displacement that axially and/or directly makes progress.

In form of implementation shown in Figure 23, clutch 601 deviates from platen 603 1 sides at housing 602 sensor spring 613 is set.By in housing inner chamber outside sensor spring 613 (the ccontaining platen 603 of housing inner chamber) being set, the thermal force of sensor spring 613 reduces, therefore since the sunken danger in the edge of the sensor spring 13 that the heat overload causes avoided.In housing 602 outsides, spring 613 also can better cool off.

The revolution that deviates from housing one side setting at operation dish spring 604 is propped up part 611 and is produced supporting roles by rivet 615 at interval, and rivet 615 axially passes the respective through hole on dish spring 604 and the housing 602 and does axially to be connected with sensor spring 613.In the present embodiment, rivet 615 is riveted with sensor spring 613 at interval.Rivet 615 connects to form between a revolution part 611 and sensor spring 613 also can to use other measure to substitute at interval.For example sensor spring 613 has axially extended connecting plate in the zone inside radially, and this plate props up part 611 with corresponding radial portion bearing and turning or even passes through the direct formation of corresponding distortion and turn round a part 611.Also can use (for example with sensor connect) articulated elements of other structure to substitute element 615 with the fixing riveted joint of sensor spring.

In form of implementation shown in Figure 24, sensor spring 713 radially extends in the inside that part 715 is propped up in the revolution that is used to operate dish spring 704.Sensor spring 713 radially is bearing on the housing 702 in zone, the inside at it.For this reason, housing 702 has corresponding slot that axially passes dish spring 704 or the connecting plate 715 that fluting extends, and this plate axially mounting sensor dish spring 713.

According to another variant embodiment scheme, sensor spring 713 limit within it has connecting plate than the district, and this plate axially passes the respective openings of dish spring 704 and is bearing in housing one side.

The regulating ring of describing in Figure 25 817 can use in the friction clutch shown in Figure 20 A to 21.Regulating ring 817 has the shaping 827 that extends radially inwardly.Shaping 827 has radially projection 827a, and it constitutes the supporting area of helical spring 826, and spring 826 circumferentially is stretched between clutch housing and the regulating ring 817.In order to guide helical spring 826 and easy for installation a ring 828 to be set, it is to disconnect or opening on periphery.Ring 828 is connected with forming section 827a radially.For this reason, shaping 827a can have along the recess of extending circumferentially and groove, and they are to constitute like this, constitutes a kind of lock of stinging when promptly they are connected with ring 828 and connects.Supporting is that axial connecting plate 826a by clutch housing constitutes to the case side of Regulation spring 826.Each axial connecting plate 826a has an axial grooving 826b with ccontaining ring 828.Therefore, grooving 826b constitutes like this, i.e. ring 828 relative connecting plate 826a.The wearing and tearing stroke of friction clutch (at least corresponding to) has axially movable possibility.For this reason, the recess and the grooving 826b (from axially) of the ccontaining ring 828 that is provided with at shaping 827a radially when being reverse geometry, meet the requirements especially, in other words, the recess that is provided with at shaping 827a is at an axially open, and grooving 826b is at another axially open.

In the form of implementation of a friction clutch 901 shown in Figure 26, operation dish spring 904 is occurred in the zone line of the matrix 904a of dish spring 904 in the supporting of detaching direction.Matrix 904a radial outside is bearing on the platen 903, and radially inwardly extends through pivoting support 905.This means, compare with known so far dish spring clutch, pivoting support 905 leave dish spring 904 matrix 904a inward flange or leave constitute dish spring 904 tongues long joint-cutting relatively far.In the present embodiment, the radial width (spacing) that radially is arranged on the matrix area of pivoting support 905 inboards and the matrix area that radially is arranged on pivoting support 905 outsides is than being 1: 2 order of magnitude.And this ratio conformed with the purpose requirement between 1: 6 to 1: 2.By this supporting, just can avoid in damage and the overload of revolution part 905 a regional dish spring matrix 904a to operation dish spring 904.

With the dotted line axial shaping 903a that drawn, it is arranged on the platen 903 in Figure 26.On platen 903, particularly the shaping 903a that is provided with in a part cam region 903b can make operation dish spring 904 relative clutch 901 centerings by this.Operation dish spring can also be by the external diameter centralising device in radially housing 902 maintenances relatively, centering, and the location is so the centering rivet or the pin 915 that are also drawn in Figure 26 just can save.Though do not draw, external diameter centering also can be realized by the connecting plate or the punching out shaping of the overhanging formation of housing 902 materials.

In friction clutch 901, the sensor spring is to constitute like this, and the matrix 913a that promptly applies power radially is located at the inside of cam 903b.On the one hand in order to support operating spring 904; In order itself to be bearing on the housing 902, sensor spring 913 has radially semi-girder or tongue on the other hand, and they extend radially inwardly from matrix 913a on the one hand, extend radially outwardly from matrix 913a on the other hand.

In the modified embodiment of a friction clutch 1001 shown in Figure 27, the power reverse with the turning power of the Separating force of friction clutch or operation dish spring applies generation by sensor spring 1013, and sensor spring 1013 is axially tensioning between housing 1002 and platen 1003.In such form of implementation, operation dish spring 1004 does not support by a pivoting support at detaching direction in tow-away zone or swing district 1005.The arrangement of propping up the dish spring 1004 on part or the supporting member 1012 in the revolution of case side is that the tension force by sensor spring 1013 guarantees.This sensor spring is to be provided with like this, promptly in the separation process of friction clutch 1001, by sensor spring 1013 be applied on the dish spring 1004 axial force greater than or become greater than the Separating force of required friction clutch 1001.Therefore must guarantee that if do not exist when wearing and tearing, dish spring 1004 always remains against in the supporting or a revolution part 1012 of case side on friction pad.For this reason must be to adjust each in axial action and power stack with the mode of described enforcement structural similarity so far.These by sensor spring 1013, by the pad spring, by may be arranged on blade spring spare between platen 1003 and the housing 1002, by operation dish spring 1004, must allocate mutually suitably by the Separating force that is used for friction clutch 1001 with by acting on the power that regulating ring adjusted spring part produces.

In friction clutch shown in Figure 28 1101, sensor spring 1113 be bearing in case side annular supporting area 1112 radially the outside.In the present embodiment, the mutual supporting between operation dish spring 1104 and the sensor spring 1113 also is arranged on the radial outside of the supporting diameter 1103a of 1104 pairs of platens 1103 of operation dish spring.In order to be bearing on the housing 1102, sensor spring 1113 has the radial outside forming section that a structure is the arm 1113b that stretches out of radially outward, it with to the described similar mode of Figure 20 to 21, by bayonet formula latching structure 1514 axially mountings on housing 1102 and guarantee not rotate.For sensor installation spring 1113, housing 1102 has corresponding axially grooved 1502b, and this is in order to form bayonet formula latching structure 1514 supporting arm of the radial outside of sensor spring 1113 axially to be imported wherein.It is by giving of sensor spring 1113 card of tightly trying hard to keep that the revolution that dish spring 1104 is placed in case side is propped up on part or the supporting member 1112.

Further explain the function of clutch with reference to Figure 27.The power of sensor spring is provided with so in this case, and promptly it is consistent with the Separating force of point of adjustment.If pad part wearing and tearing (or other position wearing and tearing) appear and therefore changed dish spring angle and and then improved disc spring force after when separated, then the dish spring at first changes up near point of adjustment around a part 1012.Because Separating force becomes and equates that together with pad spring remaining force then the dish spring turns round until till producing equilibrium of forces again between Separating force and the sensor force around the part on the platen when further separating with sensor force in this.The dish spring leaves and discharges this part so that regulate (compensation) from the part of case side in this case.In the separation stroke that continues, Separating force continues to descend, and sensor force is preponderated and propped up part 1012 extruding dish springs by platen facing to case side, and the dish spring continues revolution around a part 1012 then.When case side supporting carried out the transition to the platen side bearing, the dish spring trended towards changing its function as double-arm lever at the dish spring.Therefore temporarily it temporarily is bearing on the platen with existing Separating force on platen, and leaves from a part of case side.After separating stroke and continuing, because relevant therewith power descends, the power of sensor spring is preponderated and again the dish spring is pressed in case side and props up on the part, thus locking the controlling device and the adjustment process that is through with.After this dish spring acts on as double-arm lever again in the separation stroke that continues.The dish spring should be provided with under the situation of considering total spring force (these power act on the dish spring indirectly or directly).These power that need especially to consider are by the axial relative housing power that movably member produced in operation dish spring and corresponding compensation or the controlling device.

Form of implementation shown in Figure 28 also has following advantage, promptly be actually and be tensioned and work as double-arm lever at friction clutch jointing state dish spring 1104, and dish spring 1104 is stretched between the supporting 1103a of the supporting 1112 of case side and platen side, yet when friction clutch 1101 separates, the dish spring in fact only is bearing on the sensor spring 1113 and around supporting area 1113a and turns round, and when supporting area 1113a moved axially simultaneously, it is actually worked as single-arm lever.

Sensor spring 1113 shown in Figure 28 (as the sensor dish spring in other accompanying drawing) is on an arbitrary diameter that can be bearing in operation dish spring under the situation of suitable setting or adjustment.Therefore sensor spring 1113 can be arranged on such diameter in the supporting on the dish spring 1104, and this diameter is between the tow-away zone 1105 of the supporting diameter 1103a of platen side and case side.This outer sensor spring 1113 supporting on dish spring 1104 also can directly upwards be arranged on supporting diameter 1105 inboards of case side.Therefore the trend that requires is, the axially mounting power that is applied by sensor spring 1113 becomes big more, and then its supporting diameter 1113a on dish spring 1104 just becomes more little.In addition, when the elastic region with in fact constant power of sensor spring 1113 must become big more, it is far away more that then the supporting diameter 1113a between spring 1104 and 1113 leaves the supporting diameter 1105 of case side dish spring 1104.

Form of implementation shown in Figure 29 has a controlling device 1216, and it works in (particularly Fig. 1 to 14 was described to aforementioned figures) similar mode.The rolling that operation dish spring 1204 is bearing in two annulars is pivotally propped up between part 1211 and 1212.Part 1211 near platen 1203 is loaded by sensor spring 1213.Friction clutch 1201 has an antisticking device 1261, and it guarantees that the sloping platform of regulating ring 1217 in the operating life of friction clutch can not adhere on the opposed sloping platform of case side arrangement.In the present embodiment, these opposed sloping platforms (with similar shown in Fig. 2) be arranged on one with the housing 2 antitorque supporting rings that are connected 1225 on.Bonding meeting between sloping platform and opposed sloping platform causes such consequence, promptly can not carry out desirable compensating action to wearing and tearing again.Antisticking device 1261 is one and shakes off mechanism that it can apply an axial force on regulating ring 1217 when friction clutch 1201 separates and when wearing and tearing appear in friction pad 1207, so the adhesion that may occur between sloping platform and opposed sloping platform connection just is separated.Antiseized mechanism 1261 comprises an axial elasticity element 1262, and this part axially is connected with dish spring 1204 in the present embodiment.Element 1262 has an elastic matrix 1262a ring film shape or dish spring shape, and the radial outside of this matrix is connected with dish spring 1204.Extend the axial connecting plate 1263 that distributes along circumferentially from the radially inward edge district of annular matrix 1262a, it passes the axially grooved of dish spring 1204.In its free end district, connecting plate 1263 has limit structure (for the form of elbow 1264), opposed limit structure 1265 actings in conjunction of it and regulating ring 1217.Opposed limit structure 1265 constitutes by the groove that embeds ring 1217 or by a circumferential groove.Arrange like this at the jointing state limit structure 1264 of friction clutch and the distance between the opposed limit structure 1265, promptly at least in most of separated state of friction clutch structure 1264 and to interposed structure 1265 between do not come in contact.Limit structure 1264 just rests on the opposed limit structure 1265 when being preferably in friction clutch and separating fully, thus element 1262 can be between regulating ring 1217 and dish spring 1204 elastic tension.Guarantee like this, in case when a revolution part 1211 being produced move axially because of the wearing and tearing of pad part, forced adjustment ring 1217 leaves from the rising sloping platform of case side.In addition, (for example because the basic adjusting of piece-rate system mistake) mechanism 1261 can stop the adjusting of ring 1217 when the separation stroke is excessive.Can be implemented in dish spring 1204 elastic element 1262 when the detaching direction rotation angle is excessive like this and make regulating ring 1217 head on dish spring 1204 and tensioning, therefore form the rotation protection of regulating 1217 relative dish springs 1204.Must guarantee that also when detaching direction surpassed the point 46 of Fig. 8, regulating ring 1217 remained on dish spring 1204 opposites antitorquely,, therefore when there are not wearing and tearing in clutch disk, also may not regulate because be overcome at the stopping power that surpasses 46 o'clock sensor springs 1213 of point.This will cause the change of operation point and the change of dish spring 1204 rigging positions, and be to change to less extruding force direction.This means that operation point 41 is along the minimum value direction drift of characteristic curve 40 to label 4,5 expressions in Fig. 8.

In a kind of form of implementation of friction clutch (this clutch is made of each part shown in Figure 30 to 32), single helical spring 1326 is placed on the connecting plate 1328, and this plate and clutch housing 1302 are that one constitutes.Connecting plate 1328 is by the U-shaped otch 1302 that forms a punching out and form and stretch out shaping from the light sheet material of housing 1302.From circumferentially, connecting plate 1328 be camber line shape or tangent direction extend and preferably be positioned at identical (approximately uniform at least) axial height of shell area (distance) that is close on.From Figure 32 as seen, in the present embodiment connecting plate 1328 with about half material thickness of dislocation in housing bottom district 1302b.The width of a connecting plate 1328 is provided with like this, and promptly the helical spring 1326 that is provided with on it not only radially but also in axial part is being directed to.

Have shaping or the semi-girder 1327 that radially inwardly stretches out on the circumference by spring 1326 within it at the regulating ring 1317 of regulating the direction loading, it is in housing 1302 and 1304 extensions of dish spring.Semi-girder 1327 radially inner sides have axially a fork part or a U-shaped shaped portion 1327a, the both sides of its two axial prong 1327b fastening spring guide plates 1328.Therefore these two prong 1327b axially pass the otch 1302a of housing 1302.Regulation spring 1326 is bearing on shaping 1327a or its prong 1327b.

With previous drawings describe similar, regulating ring 1317 is bearing on the opposed rising sloping platform 1324 that is formed by housing 1302 punching out by its rising sloping platform.And the housing punching out position that constitutes opposed rising sloping platform is this spline structure, and promptly it forms a ventilating hole 1324 in the clutch sense of rotation.Owing to adopt such structure, when corresponding friction clutch rotated, by compulsory air ventilation, itself was cooled off clutch preferably.Especially therefore the regulating ring 1317 that is made of plastics also is cooled, thereby can obviously reduce the thermal load that these members cause.

According to another modified embodiment, the sensor force that affacts on the operating spring of friction clutch can be applied by the blade spring spare that for example is provided with between friction clutch housing and platen, these blade spring spares can make platen be connected with housing antitorquely simultaneously, and axially can relatively move limitedly.In this form of implementation, not only the sensor spring is not had specific (special) requirements, and the blade spring spare 9 of the friction clutch 1 shown in Fig. 1 and 2 can also constitute like this, i.e. its also subsidiary effect of bearing sensor dish spring 13.Therefore, not only sensor spring 13 but also rotating support ring 11 also can save.Blade spring spare 9 must constitute so thus, and promptly when actuating friction clutch 1 and pad part did not did not wear and tear, the revolution that operation dish spring 4 remains against case side was propped up on the part 12.Yet, in case when corresponding wearing and tearing appear in friction pad 7 (therefore the Separating force of dish spring 4 increases), blade spring spare 9 must can make dish spring 4 corresponding wearing and tearings regulate.Be installed in the interior blade spring spare 9 of friction clutch preferably has straight line at least on friction clutch or the needed maximal regulated stroke of platen power-stroke characteristic curve.This also means, with Fig. 9 described similar, blade spring spare 9 should have a characteristic line section 48 according to characteristic curve 47 or 47a.

The present invention is not limited to also comprise deformation program on the embodiment who describes and narrate that these deformation programs are to form by being combined in feature or the element described among each different embodiments.In addition, all can be used as independent invention by new feature of describing in the accompanying drawing or new function itself.

The friction clutch of describing in 34 at Figure 33 1601 have a housing 1602 with one therewith housing antitorque be connected and axially can limited mobile platen 1603.An extruding dish spring 1604 axially is stretched between platen 1603 and the housing 1602, this dish spring can be around annular pivoting support 1605 revolutions by housing 1602 supportings, and platen 1603 is loaded to an opposed platen 1606 of fixedlying connected with housing 2 (for example flywheel) direction, thus, the friction pad 1607 of clutch disk 1608 is clamped between the friction surface of platen 1603 and opposed platen 1606.

Platen 1603 is done antitorque the connection with housing 1602 in order to the circumferential or tangential articulated mounting of sheet spring 1609 forms.In the present embodiment, clutch disk 1608 has so-called pad spring sector 1610, it guarantees that running torque is little by little set up when friction clutch engages, move axially at the limited of opposite direction by two friction pads 1607 like this, and the axial force that acts on the friction pad 1607 is improved gradually.Yet, also can use a kind of like this clutch disk, wherein friction pad 1607 is in fact axially stacked at least one supporting disk rigidly, and in other position (for example between dish spring 1604 and platen 1603) of pad spring sector 1610 alternative is set.

Dish spring 1604 has an annular matrix 1604a who applies extruding force in the present embodiment, extends radially inwardly out operation tongue 1604b from matrix 1604.Therefore dish spring 1604 is to install like this, and promptly its zone of being provided with continuously with radial outside loads platen 1603 and can be with the zone of the radially inner side of continuous setting around pivoting support 1605 revolutions.Pivoting support 1605 comprises two revolution parts 1611 and 1612, and here they are made of wire rings, and the dish spring is by axial clamping or be stretched between them.For the rotation that ensures operation dish spring 1604 with for the centering of metal ring 1611,1612 relative housings 1602 and fixing of theirs, the holding device of rivet spare 1615 forms is fixed on the housing, each rivet spare all has an axially extended jack-post 1615a, and rivet spare passes in the space that is arranged between the adjacent dish languid and extends.

Clutch 1601 has the controlling device that a compensation is is axially worn and torn on the friction surface of platen 1603, opposed platen 1606 and friction pad 1607, the restricting means 1617 that it is arranged on the wear compensation device 1616 between extruding dish spring 1604 and the platen 1603 by one and limits the separation stroke of platen 1603 is formed, and restricting means 1617 is made of stroke sensor.

The restricting means 1617 that plays the wear sensor effect all has a sleeve 1618, and it is placed in the through hole 1620 of platen 1603 antitorquely.Sleeve 1618 constitutes 1621, two the sheet spring spares 1622 in a slit and axially passes this slit extension.Sheet spring spare 1622 supports mutually, and wherein at least one sheet spring spare overarches, and best two sheet spring spares become opposite opposed arch.Sheet spring spare 1622 is placed in the sleeve and therefore and can overcomes the relative sleeve 1618 of predetermined surface friction drag moving axially at clutch 1601 with the tensioning of determining of giving.The axial length of sheet spring spare 1622 is to select like this, promptly the clutch member of the relative axial restraint of these sheet spring spares (in the present embodiment the outer edge area 1623 of housing 1602) relatively has a definite gap 1624 in the friction clutch 1601 that engages, and it is consistent that this gap and predetermined platen 1603 separate stroke.In the friction clutch that engages, sheet spring spare 1622 rests on the opposed platen 1606 with its end 1622a that deviates from housing 1602, therefore guarantee when friction pad 1607 wearing and tearing that platen 1603 can fill up the part wearing and tearing according to this and do moving axially of relative sheet spring spare 1622, and opposite with the friction interconnect function of 1618 in sheet spring spare 1622 and sleeve, the most handy plastics of sleeve or friction material are made.

In the present embodiment, through hole 1620 is arranged in the platen cam 1625, by being pressed into, sleeve 1618 not only make it axially but also make circumferentially and all fix in the through hole 1620, cam 1625 extends radially outwardly, and each sheet spring spare 1609 is hinged on the cam 1625 by a rivet connection 1609a.Sleeve 1618 also can be avoided like this moving of opposed platen 1606 directions, and promptly sleeve 1618 has a crimping 1618a in its end towards housing 1602, and by this crimping, sleeve 1618 can be bearing on the platen 1603.Sleeve 1618 can be avoided like this to outer the moving of housing or clutch cover 1602 directions from through hole 1620, and promptly (shown in Figure 33 dotted line) sheet spring 1609 and sleeve 1618 part radial overlaps can axially be stretched in the through hole 1620 if necessary securely.In addition, the rotation of sleeve can stop like this, and promptly sleeve has a moulding section, step particularly, the zone 1619 of its ccontaining spring 1609 and sleeve overlap joint.

Wear compensation device 1616 has a compensation member that is loaded by dish spring 1604, and it is the form of the plate ring 1626 in U-shaped cross section, and Figure 37 is its top view.Axial protuberance 1628 or a plurality of protuberance 1628 that compensation member 1626 has at least one annular at base plate 1627 towards the side of dish spring 4, these protuberances 1628 are preferably along circumferentially uniform and extrude groove by sheet material and constitute.Fan-shaped protuberance 1628 can guarantee, in the zone between circumferentially adjacent protuberance and constitute the radial passage between dish spring matrix 4a and compensated loop 1626, these radial passages can form an air passageways that is used to cool off.Especially as seen from Figure 34, compensated loop 1624 relative platen 1603 centerings.For this reason, platen 1603 has at least one step 1629, and it is centrally located the also axially extended wall of compensated loop 1626 radially inner sides portion 1630 relative platens 1603.Step 1629 can be made of a closure surfaces along extending circumferentially, perhaps also can be made of a plurality of sectors along circumferentially space setting.In addition, compensated loop 1626 has one in radial outside and axially extended wall portion 1631, it and inwall 1630 and annular free chamber 1626a of base plate 1627 common formations.Compensated loop 1626 radial outsides have radially semi-girder or cam 1632, and they constitute bounding means.The opposed bounding means 1633 of these bounding meanss and axially movable member (it is the form of the sheet spring spare 1622 of wearing and tearing sensing element 1617) synergy.Opposed bounding means 1633 is made of the nose that sheet spring spare 1622 is shaped, and it radially inwardly points to and overlaps with semi-girder 1632.Therefore compensated loop 1626 is leaving moving axially of platen 1603 directions, that is moving then owing to opposed bounding means is restricted to housing direction.

A compensation device 1634 is set between compensated loop 1626 and platen 1603, it can make compensated loop 1626 regulate automatically and play self braking and self-locking during in clutch when friction clutch 1601 separates and when the wearing and tearing of pad part occurring, therefore guarantee: definite axial position of compensated loop 1626 relative platens 1603 maintenances when friction clutch 1601 is in jointing state.Only the position of this qualification just changes when the wearing and tearing of pad part correspondingly appear in the separation process neutralization.

Compensation device 1634 comprises the circumferentially uniform wedge spare in a plurality of best edges to 1635,1636, and they are contained in the annular free chamber 1626a of plate ring 1626.The wedge spare 1636 that is bearing on the ring surface 1637 of platen 1603 axially movably is connected with loop 1626 antitorque ground.For this reason, the shaping that loop 1626 has groove 1638,1639 forms in its zone that extends axially wall portion 1630,1631, this shaping constitutes protuberance in the zone of free chamber 1626a, and they embed in the corresponding cooperation recess or groove 1640,1641 of wedge spare 1636.Groove 1640,1641 or shaping 1638,1639 extending axially at friction clutch 1601.Wedge spare 1635 axially is being contained between the bottom 1627 and wedge spare 1636 of loop 1626 substantially.Wedge spare 1635 and 1636 is formed in the rising sloping platform 1642,1643 that extending circumferentially rises in the axial direction, supports relatively by a pair of wedge spare 1635,1636 of these sloping platforms.Wedge spare 1635 is bearing on the other hand on ring 1626 and the bottom 1627 and can be relative to ring 1626 along circumferentially moving.Rising sloping platform the 1642, the 1643rd, mutual tensioning.For this reason, the power accumulator of helical spring 1644 forms is set in ring cavity 1626a, it with an end bearing one with the ring 1626 antitorque wedge spares that are connected 1636 on, being bearing in one with its other end can be on the wedge spare 1635 that circumferentially moves.In order to maintain power accumulator 1644, wedge spare 1635,1636 is equipped with protuberance 1645,1646 in its end towards the corresponding force accumulator, and protuberance 1645,1646 embeds in the spring ring and therefore maintains spring end.This outer spring 1644 is by the wall section 1630 and bottom 1627 guiding of ring 1626.

Can guarantee that in the present embodiment compensated loop 1626 can not rotate relative to platen 1603.For this reason, as shown in Figure 36, the axial protuberance of pin 1647 forms is set on platen 1603, and pin axially is passed in fluting 1648 extensions that semi-girder 1632 zones are provided with.By this rotation safty device, when working, friction clutch can ensure that the limiting area of connecting plate 1632 always is positioned at restriction nose 1633 belows of sheet spring spare 1622.

In the present embodiment, wedge spare 1635,1636 is made by a kind of heat resistant plastice (for example a kind of thermosetting property or thermoplastic), can also carry out fibre strengthening to it and handle.Therefore the wedge spare 1635,1636 that plays the adjusting element effect can be produced as the spray part with simple mode.But at least one also is favourable when making by friction material (for example filling up the part material) in a pair of wedge spare 1635,1636.Yet wedge spare or adjusting element 1635,1636 also can make plate type member or sintered part.The angle of climb of rising sloping platform 1642,1643 and extended length are to be provided with like this, promptly guarantee can compensate in the whole life-span of friction clutch 1601 occurring wear on the friction surface of platen 1603 and opposed platen 1606 and friction pad 1607.The angle of climb 1649 of rising sloping platform 1642,1643 or the angle of wedge 1649 relative planes perpendicular to the friction clutch spin axis, be chosen such that the rubbing action that promptly produces should stop the slip between sloping platform when rising sloping platform 1642,1643 compresses mutually.Material according to rising sloping platform 1642,1643 zones is right, and this angle 1649 can be preferably 10 ° in 5 ° to 20 ° scope.Circumferentially movably wedge spare 1635 is to settle like this, and promptly its wedge point points to sense of rotation 1650.

Should be provided with like this by the power accumulator 1644 of rising sloping platform 1642,1643 and the tensioning of the angle of climb 1649 generations, promptly act on and move required power less than the wearing and tearing sensing element 1622 of restricting means 1617 axially making a concerted effort on the regulating ring 1626.

In addition, must consider when dish spring 1604 is set: being applied to extruding force on the platen 1603 by the dish spring must increase a tension force value that moves the required power value of wearing and tearing sensing element 1622 and increase a sheet spring 1609 of tensioning between housing 1602 and platen 1603.In addition, each member must be provided with like this, promptly the part wearing and tearing between dish spring 1604 and the supporting ring 1626 and between wearing and tearing sensing element 1622 and the opposed platen 1606 or the wearing and tearing of the device between wearing and tearing sensing element and housing 1602 to compare with the wearing and tearing of pad part 1607 be small.

For fear of between the rising sloping platform 1642,1643 or between regulating element 1635,1636 (Figure 35) produce undesirable adjusting, at least in the zone of a rising sloping platform 1642,1643 little protuberance is set, these protuberances are hooked on the other sloping platform.Simultaneously, these protuberances can be provided with like this, can realize the adjusting of a compensate for wear, and can stop the mutual slip of sloping platform again.Two kinds of sloping platforms all have the protuberance of catching mutually to meet the requirements especially.These protuberances for example can the type exterior feature of the sawtooth like shape of low height constitutes by stretching out very, and relatively moving of 1642,1643 of sloping platforms only can be taken place in the wear adjustment ring for it.A kind of such type exterior feature schematically illustrates with the part area that sloping platform 1642,1643 extends in Figure 35, and label is 43a.The sort ofly only there is a rising sloping platform 1642,1643 to have under the situation of protuberance using, these protuberances can be provided with like this, to be them with the material that constitutes other rising sloping platform compare has higher hardness, so can clamp-on and firmly grasp those their rising sloping platform protuberances of supporting at least a little.

Thereby lose its tension force for fear of a spring 1622 arch or corrugated because of engaging process produces very high temperature on platen 1603, sleeve 1618 is preferably made by a kind of heat-conducting property difference and the high material of friction factor.Wedge spare 1635,1636 can be made by same material.

For cooled clutch preferably, particularly in order to cool off platen 1603 preferably, can platen 1603 be provided with radially extend and along the groove that circumferentially distributes, in Figure 34, be represented by dotted lines, label is 1651.From circumferentially, this radial groove 1651 always be arranged on two adjacent wedge spares between and between ring 1626 and platen 1603, extend.In the zone of spring 1644, ring 1626 can have the axial cut-outs of 1627 beginnings from the bottom, therefore constitutes the radial passage at dish spring 1604 with between encircling 1626.

In order to improve the wear resistance of different bearing positions, can wearing layer be set at respective regions, for example chromium plating is hardened, is coated with molybdenum or also wear-resisting especially member can be set in the contact area.For example can wearing and tearing sensing element 1622 on and with housing 1602 and opposed platen 1606 by putting plastic made tile is set in the zone.

Applying the sheet spring 1609 of torque to the platen 1603 should tensioning like this between platen 1603 and housing 1602, and promptly it moves platen 1603 when friction clutch 1601 separates to housing 1602 directions.Therefore guarantee, in fact whole separated state or before restricting means 1617 works ring 1626 lean against on the dish spring 1604 always.

Separation stroke at the lip of the tongue 1604c zone internal clutch is preferably selected like this, and promptly in the clutch that separates, the outward edge of dish spring 1604 slightly leaves a bit from encircling on 1626.This also means, when friction clutch 1601 separates because dish spring 1604 and execute the dish spring stroke that carries diameter region at platen and leave stroke 1624 greater than the platen of determining by stroke restricting means 1,622 1603.

The relative position of each member of describing in Figure 34 is consistent with the new state of friction clutch.In axial wearing and tearing, when friction pad 1607 wearing and tearing, just move towards the direction of opposed platen 1606 position of platen 1603 especially, according to this, at first exist tapering to change and according to this, the dish spring changes in the extruding force that the jointing state of friction clutch 1601 applies, and mainly is to increase.This variation causes that the axial position of platen 1603 changes with respect to the wear sensor 1622 of axially mounting on opposed platen 1606.Because the disc spring force of effect on ring 1626, so this ring 1626 is just followed platen 1603 because of moving axially that the pad wearing and tearing cause.According to this, this ring stop zone 1632 of 1626, vertically from opposed position-limiting action and its zone that is shaped as wear sensor 1622 noses 1633 leave, and leave one basic with fill up the consistent distance of wearing and tearing.This compensated loop 1626, in engaging process, relative platen 1603, keep its axial position constant, because it by dish spring 1604 by direction imposed load towards platen 1603, and wear compensation device 1634 self braking in engaging process, that is make axial locking.When friction clutch separated, platen carried and moves being executed on the direction of housing 1602 by blade spring 1609, until wear sensor 1622 by put on the housing or housing stop zone 1623 on.This with platen 1603 leave stroke consistent separate stroke, the relative platen 1603 of ring 1626 axial positions remains unchanged always.Continuing under the separation process situation, it is motionless that platen 1603 axially keeps, and in contrast, encircle 1626 and carry the detaching motion of following the dish spring in the diameter range on axial executing, and always with arriving, the stop zone 1632 of ring 1626 is again by on the opposed stop zone 1633 of putting wear sensor 1622.Moving axially by wedge spare 1635 of ring 1626 of compensation causes that it is by spring 1644 imposed loads.1635 of this wedge spares move at circumferencial direction relative to wedge spare 1636 always, push up up to ring 1626 on the opposed stop portion 1633 of wear sensor 1622 till the tensioning.Under the present embodiment situation, leaving by blade spring 1609 of platen 1603 provides, and this blade spring 1609 so is installed between housing 1602 and the platen 1603, promptly produce one and axially give tensioning, and this gives tensioning platen 1603 is pressed to housing 1602.If dish spring 1604 continues to turn round on detaching direction, so, this dish spring just leaves from regulating ring 1626 with the zone that it directly makes progress the outside, because regulating ring (as already described) is braked in the axial direction by wear sensor 1622 relative platens 1603.Dish spring 1604 relative adjustment rings 1626 this of generation are small leaving at least during separation process, are particularly advantageous for regulating system 1617+1634.

The present invention transfers device 1617+1634 to guarantee, the regulating action on supporting ring 1626 is always carried out according to the pad wear extent by adjusting wedge spare 1635,1636.This is because regulating ring 1626 is to be axially to clamp between the controlling device of wedge spare 1635,1636 and the wear sensor 1622 in structure, according to this, just can prevent the compensation member generation regulated quantity bigger than corresponding wear extent of ring 1626 shapes.In addition, configuration by controlling device of the present invention just can guarantee, even in the segregating unit zone (as the dish languid 1604b of portion) or when under platen axial vibration situation, over-travel (uberweg) occurring, controlling device 1617+1634 can not regulate, because, wear sensor 1622 is also under the rigid collision situation, and wear compensation device 1634 axially mountings by self braking are on the housing 1602 relative with platen 1603, and by opposed limited part 1632 supportings.That is under the separated state of friction clutch, may act on the wear sensor 1622 and transmit power towards the axial force of opposed platen 1606 directions greater than the closure between abrasion sensor 1622 and platen 1603, simultaneously, relative this platen 1603 of wear sensor axially is not moved.

Using controlling device of the present invention can guarantee, during the Complete Service Life of clutch, in fact this dish spring has a tension position that reality is constant in identical characteristic line regional work and at the jointing state of friction clutch 1601, therefore, on platen 1603, apply the extruding force of a practical stability.Just can use a dish spring that during separating stroke, has the force characteristic line that successively decreases according to this, and preferably and a clutch disk combined, the pad spare of this dish 1607 is by spring sector 1610 and relatively by elastic tension, therefore, the Separating force that effectively applies can be placed on the low relatively level, and during the clutch operating life, as long as pad spring characteristic not obvious changing between life of clutch, then above-mentioned Separating force can actually remain unchanged.When such clutch separation, dish spring 1604 just around its housing supporting 1605 revolutions, simultaneously, gives in fixed a part of axial separation stroke at platen 1603,1610 unloadings of spring sector, the axial force that is applied by spring sector 1610 helps the separation process of friction clutch 1 thus.That is mean, relatively at the engagement positio of clutch 1601 by the power that the rigging position of dish spring 1604 and blade spring 1609 is caused in theory, only need a less maximum separation power.In case the elastic region or the relaxation area of sector 1610 have been exceeded, then friction pad 1607 is released, simultaneously, because the characteristic line zone of successively decreasing, (dish spring 1604 work in this district), also the Separating force that will apply significantly than with Figure 34 in assembling point or the corresponding Separating force of rigging position reduced.In continuing separation process, Separating force further descends, and drops at least, and dish spring 1604 is preferably till the minimum value or low valley point of sinuso sine protractor line.

The controlling device 1617+1634 that in Figure 33 and 34, describes, can so dispose by advantageous manner, promptly, in the friction clutch 1601 that rotates, each spring pitch of the laps of regulating dish spring 1644 is bearing on the outer wall 1631 of regulating ring 1626, by spring 1644 the adjusting power that applies on the circumference then since the surface friction drag that between spring pitch of the laps and regulating ring 1626, produces be reduced or even be cancelled fully.That is in fact spring 1644 can become stiff owing to the frictional force that spring action is reduced under friction clutch 1601 rotation situation.In addition, regulating wedge spare 1635 can be prevented to rotate by radial support on the wall 1631 of regulating ring 1626 and by the frictional force in wedge spare 1635 and 1626 generations of regulating ring equally by the centrifugal force that acts on thereon.Can realize that according to this in being higher than the revolution zone of idling of IC engine rotating speed, this wear compensation device 1634 can be owing to spring 1644 rotates at least.Like this, friction clutch 1601 can so be provided with, i.e. friction pad wearing and tearing are only carried out during at actuating friction clutch 1601 in racing speed or under at least near the racing speed situation.The locking of regulating ring 1626 also can so realize by correspondingly disposing wear compensation device 1634, that is, only in the state of rest of internal-combustion engine, that is do not change or under very low revolution situation, can carry out the adjusting of pad wearing and tearing at friction clutch 1701.

Constituting the member 1635 of regulating sloping platform, material between 1636 to and and the construction material of these member mating reactions, preferably so selected, promptly, during the running life of friction clutch, not can sloping platform and and the member of sloping platform mating reaction between the stickiness that overslaugh is regulated takes place.For avoiding such stickiness, at least one a this member and coating is set in the zone of sloping platform or bearing surface at least.

Connect for avoiding between rising sloping platform and opposed rising sloping platform, producing to adhere to, at least one antisticking device can also be set, it applies an axial force on these sloping platforms or regulating element when friction clutch separates or when wear adjustment, this power is separated sloping platform or drawn back.

New state at friction clutch 1601, that is before clutch is packed on the opposed platen 1606 by centre installation clutch disk 1608, the position of representing among this wedge spare 1635 relative Figure 35 is on the position that a relative wedge spare 1636 further pulls back, therefore, regulating ring 1626 has its position that maximum is pulled back on the direction of platen 1603 also according to this, and these platen 1603/ regulating ring Unit 1626 need minimum axial arrangement space.For wedge spare 1635 was remained on its position of pulling back before assembling friction clutch 1, this wedge spare 1635 has the mating area that is used for a slewing gear or stopping device, and its structure is a groove 1652.The stopping device of this form can be provided with when making or assemble friction clutch 1601, and after friction clutch 1601 assemblings, takes away from flywheel 1606 again, and therefore, controlling device 1634 just can activate and turn round.In the present embodiment, on regulating ring 1626, be provided with the microscler slot 1653 that along the circumferential direction extends,, can allow the mating area of stopping device or screwing tool import and stick in the groove 1652 by it.Simultaneously, must have an extension part in the elongate recesses 1653 of circumferential directions, it is corresponding with wedge spare 1635 rotation at the wear adjustment angle of maximum possible in a circumferential direction.And in the friction clutch of new state and at circumferencial direction, keep the wedge spare 1635 of its position of pulling back to guarantee to remain on this position by making regulating ring 1626 at the wear sensor 1622 of its position of pulling back.The connection set of self regulating between wear sensor 1622 and platen 1603 is structure so, be greater than making a concerted effort of acting on ring 1626 in order to make wear sensor 1622 move necessary locomotivity relative to platen 1603 promptly, this power is to produce by wedge spare 1635 being executed the spring 1644 that carries.

In the embodiment who presses Figure 33 and 34, sloping platform 1643 can also directly be made of ring 1626, and for example the surface 1643 that tilts by punching out constitutes, and simultaneously, ring 1626 must be rotated relative to platen 1603 by spring.This wedge spare 1636 in this enforcement structure be with platen 1603 draw turn round setting or directly make thereon.In addition, in this form of implementation, the bounding means of being arranged to semi-girder 1632 along the circumferential direction is to regulate the corresponding prolongation of corner with essential ring 1626, to guarantee keeping a stable axial qualification that runs through the friction clutch operating life between wear sensor 1622 and ring 1626.In the end in the enforcement structure of Miao Shuing, this regulating ring 1626 can also simple mode rotate from radially outer when assembling friction clutch 1601, and rotate by the position limit arm 1632 that extends at circumferencial direction especially, this semi-girder 1632 can be approaching by the radial direction through hole that is provided with in the shell of clutch housing 1602.This radial direction through hole, transmission of torque protuberance 1625 and blade spring 1609 that also can ccontaining especially platen 1603.In addition, the advantage of controlling device of the present invention is that its principle also can be applied in so-called stretching or the friction clutch, at this moment, spring is bearing on the clamshell pivotally at the fringe region of its radially outer, and with its radially the fringe region that is provided with of the inside to the platen imposed load.This clutch is depicted among Figure 38.A wear compensation device 1734 is set between dish spring 1704 and platen 1703, and it is similar to Figure 33 and 34 structures of describing.This regulating ring 1726 is again by sensor element 1717 and wear sensor 1722 synergies.The adjusting of these wear sensor 1722 relative platens 1703 rests on housing or the housing 1702 by stop zone 1722a and realizes.This wear sensor 122 also is loaded with bounding means 1733, and it limits the axial stroke of platen 1703 in separation process.For the controlling device that makes Figure 38 has the performance of a no problem, this ring 1726 has a relative wear sensor 1722 at least and makes small axially movable possibility.This point can so realize, a corresponding spacing link 1733a who has the gap promptly is set between wear sensor 1722 and ring 1726, perhaps, also can so realizes, be that ring 1726 has the radial zone at axial elastically deformable, that is have a flexible pliability.

In a modified embodiment of not describing, wear sensor 1722 can be not with housing 1702 with dish spring 1704 synergies and at least one axially on (and preferably at least under clutch situation) act synergistically.Simultaneously advantageous manner can be, is arranged on the housing 1702 at least and executes on the radial height of carrying diameter or dish spring supporting diameter near the dish spring at the bounding means between wear sensor 1722 and the dish spring 1704.For drawing clutch, according to the purpose requirement, the supporting diameter of wear sensor on the dish spring can be greater than the supporting diameter of dish spring on platen.

Among the embodiment who describes in Figure 39, wear sensor element 1817 is directly installed on the matrix of platen 1803.Wear sensor 1822 has stop zone 1822a, it and shell area 1823 mating reactions that constitute opposed bounding means.This housing district 1823 is an integrative-structure with fixing device 1802a, and by fixing device 1802a, dish spring 1804 is placed on the housing 1802 pivotally.In the present embodiment, fixing device or holding unit 1802a are made of the integral type connecting plate that case material constitutes, and it extends by dish spring 1804 vertically.On the outside radial extension of the wear sensor 1817 of the radial zone setting of dish spring matrix 1804a, be provided with wear compensation device 1834.

In the embodiment of Figure 39, wear sensor 1822 axially not with housing 1802 or shell area 1823 mating reactions, and at least can be at an axial direction upper support on dish spring 1804, preferably at least under the clutch situation.For this reason, this dish spring 1804 can have one axially grooved, wear sensor 1822 extends through this groove, in order that stop zone 1822a axially is not bearing on the opposed stop zone 1823 at the jointing state of friction clutch, and is bearing on the dish spring 1804.When friction clutch separated, this stop zone 1822a can be from 1804 clutches of dish spring because, stop zone 1822a be arranged on one than dish spring 1804 on the little diameter of the supporting diameter on the platen 1803.This be because, stop zone 1822a is the supporting diameter between platen 1803 and dish spring 1804 relatively, closely is positioned near the swing diameter of dish spring 1804.

By friction clutch organization plan of the present invention, not only can be but also can be by reducing Separating force especially by using the operating life that thicker friction pad improves friction clutch (that is realize by improving axial pad wear volume), and be so to realize: it is combined to use power storage and at least one spring assembly that has the power-stroke characteristic line that successively decreases in friction clutch separation stroke, this spring assembly with act on power storage adverse effect on the platen, and during at least a portion friction clutch operational stroke or platen stroke, have one at the joint of friction clutch and when separating and make the effect that increases (foundations) or decline (elimination) by the friction clutch torque transmitted gradually.This spring assembly requires to be connected in series with the extrusion spring (as the dish spring) of friction clutch according to purpose.That is can realize that by friction clutch organization plan of the present invention a fairly obvious ground Separating force descends, and this descends, and maintenance exists or does not change during the operating life of friction clutch, this means, remain in the narrow relatively tolerance range.In addition, in friction clutch of the present invention, can use the dish spring that its working zone has steep relatively power-stroke characteristic.This dish spring then can cause very strong increasing of the Separating force relevant with the pad wearing and tearing in traditional clutch.

In clutch,, at first move along the direction of curve 40 towards maximum value 41a with the corresponding point 41 of the jointing state of friction clutch (Fig. 8) along with the pad wearing and tearing that increase without controlling device of the present invention.In separation process, put 41 Separating forces and just begin to descend, but in general, the level of Separating force curve increases with respect to the Separating force curve of friction clutch at the new system state up to this.This means that zone 43 is moved to the left, match until point 41 and maximum value 41a.Point 44 also correspondingly moves along characteristic curve 40.Under pad part further abrasion condition, just move towards the direction of a 41b gradually with the assembling point of the corresponding operation dish of friction clutch jointing state spring from maximum value 41a, therefore, the extruding force that is applied by the dish spring reduces gradually.Be operated extruding force that the dish spring applies at a 41b place consistent with the extruding force that applies during for new state at point 41 place's friction clutches.In case maximum value 41a is exceeded, then Separating force increases during a part of clutch operating stroke at least in separation process.When reaching maximum wearing and tearing stroke that allows or wear point 41b, there is an increase in Separating force 43a during whole separation strokes.The raising of this Separating force, when as when having a pad spring or a pad spring Replacement Part as described in Fig. 8, still keep existing.

Under configuration friction clutch and particularly its controlling device situation, must consider that the bent axle of internal-combustion engine can cause on flywheel axially and the swing vibration that they also will be delivered on friction clutch fixing on the flywheel.Can move on no problem ground in order to make friction clutch or controlling device, that is to say can be owing to undesirable adjusting takes place in this vibration, so under embodiment situation according to Fig. 1 to 27, that is fully usually have in the controlling device embodiment of force transducer, the adjusting power of this force transducer must be greater than the supporting force that may act on the force transducer.These supporting forces cause owing to quality and acceleration product, that is the quality by main dish spring regulating ring or regulating element particularly, corresponding a part of force transducer quality and in case of necessity in addition the quality of member multiply by the axial acceleration of the maximum possible of these members or element, and acceleration is since flywheel axially and flexure vibrations cause.Like this, for example in an embodiment of pressing Figure 27, sensor dish spring 1013 is bearing on the clutch compressing disc 1003, also must consider the inertia of this clutch compressing disc 1003.That is must often guarantee that the power that is applied by the sensor spring is greater than the power that acts on this spring, this power is the quality that be multiply by these members by the axial acceleration of maximum possible, and these members are owing to its inertia acts on the sensor spring.These inertial force may play deleterious effects in the operation period of friction clutch with special separated state at friction clutch especially.

In embodiment, and under configuration wear sensor and wear compensation device situation according to Figure 34 to 39, same, because each member inertia and the power axial and that rotational vibrations produces that acts on these members must take in.

Like this, usually under the friction clutch situation of a band of configuration combined type wear compensation device, always should consider the quality of element, if its go up may transmit axial or rotational vibrations and these oscillating actions on compensation device.In embodiment, should consider the influential member of those performances especially to sloping platform mechanism according to Figure 33 to 39.

In Figure 40, show a flywheel that separates 1401, this first or main flywheel piece 1402 (it can be fixed on the bent axle of a not shown internal-combustion engine) have one second or secondary flywheel piece 1403.On the second flywheel piece 1403, and under the situation of a clutch disk 1405 of centre arrangement, fix a friction clutch 1404.By it, one equally not the gearbox of expression just can engage and separate.Flywheel piece 1402 and 1403 is rotatable mutually the arrangement by bearing 1406, and this bearing 1406 is placed in the inside of through hole 1407 diametrically, and hole 1407 is used to pass fixing bolt 1408, so that the first flywheel piece 1402 is installed on the live axle of internal-combustion engine.Acting on damping device 1409 between two flywheel pieces 1402 and 1403, it has helical compression spring 1410, and other is put in an annular chamber 1411, and this chamber 1411 constitutes a toroid zone 1412.This annular chamber 1411 to small part is filled with a kind of resisting medium (as oil or grease).

This primary flywheel piece 1402 preferably constitutes by the member 1413 that a sheet material is made.This member 1413 has a flange shape zone 1414 of substantially radially extending, and this zone radially is equipped with an integrally formed and extension part vertically 1415 inward, and it is surrounded by through hole or eyelet.The rolling bearing 1406a of this single-row rolling bearing 1406 is installed on the radially outside of end portion of the portion of extending axially 1415 with ring 1416 in it.The outer shroud 1417 of this rolling bearing 1406a is supporting the second flywheel piece 1403 of being arranged to substantially flat and discoid body.For this reason, this flywheel piece 1403 has the perforate of a centering, wherein, is equipped with bearing 1406a.This zone 1414 of substantially radially extending radially carries out the transition to the zone 1418 of a shell construction outward, and it also surrounds power storage 1410 at least in part by its excircle at least and guiding is supported it.Fixing shell construction body 1419 parts surround the circumference of power storage 1410 on zone 1418.Body spare 1419 is with plate body 1413 welding (at 1420 places).The zone 1412 (seeing at circumferencial direction) of this toroid is divided into single holding area, has the power of being provided with storage 1410.These single holding areas (seeing at circumferencial direction) are separated by the Shi Zaiqu that is used for power storage 1410, and Shi Zaiqu can constitute by the bag part of punching out in plate 1413 and shell construction body 1419.This is supported by clutch housing (lid) body with second flywheel piece Shi Zai district 1421 that be connected and that be used for power storage 1410.

This Shi Zai district 1421 constitutes by arm spare radially 1421, and it is on the axial region 1423 that is placed in clutch housing (lid) 1422 under the present embodiment situation.And in radially snapping in ring cavity 1412 and snap in adjacent power at circumferencial direction and store between 1410 the end.This axially extended cap zone its part of 1423 usefulness 1423a covers or surrounds the second flywheel piece 1403 and at this flywheel piece prominent product by being provided with for example in part 1423a, (its holding is in the corresponding recesses of flywheel piece 1403) or by the connection that fixes of an other fixed form.

The clutch housing 1422 of this centering on the external frame of flywheel piece 1403 in its end away from Shi Zai district 1421, is equipped with an annular region 1426 of substantially radially arranging inward, keeps a dish spring 1427 that plays two arm bar effects on it pivotally.Its zone of radially continuing to dispose outward of these dish spring 1427 usefulness is to a platen (plate) 1428 imposed loads, and according to this, the arm friction pad 1429 of clutch disk 1405 just axially is being clamped between the second flywheel piece 1403 and the platen 128.A pad spring 1465 is set between friction pad 1429.

As seen from Figure 40, the zone 1412 of this annular chamber 1411 and toroid thereof preferably radially is placed in the outside of the second flywheel piece, 1403 external frames.According to this, this is used for that the first flywheel piece 1402 is hinged on member 1413 (it is adjacent with internal-combustion engine) on the live axle of internal-combustion engine and that be equipped with toroid zone 1412 and the second flywheel piece 1403 (it radially is positioned at inside of annular chamber 1411 and radially has quite long extension part) can be under the situation of intermediate cavity of formation or air gap 1430, in fact can be directly opposed on the contrary, that is in fact with a less spacing arranged adjacent, therefore, just can realize one by flywheel 1401, the assembly that clutch 1404 and clutch disk 1405 constitutes is compact structure mode very in the axial direction.The sealing of this annular chamber 1411 guarantees by a Sealing 1431, and it works between the outer surface of the zone, the inside of radial wall 1419 and housing 1422.

By favourable mode, this intermediate cavity 1430 can be used to cool off flywheel 1401, and imports one cooling air flow by this intermediate cavity 1430 in flywheel.In order to produce one such cooling air eddy current, this second flywheel piece 1403 radially and in friction pad 1432 the insides is being equipped with axial fluting 1433, and it is in the direction extension and feeding intermediate cavity 1430 of the member 1413 that starts pusher side.In order to improve cooling, this second flywheel piece 1403 can have axially listens port 1435 in addition, it radially also will be positioned at more the outside and be connected with intermediate cavity 1430 in that side away from friction pad 1432, and its (1435) is repeatedly filled up 1432 outside and gone in flywheel piece 1403 pass-out on the side of clutch 1404 radially being positioned to rub.Be positioned at port radially or the place of 1433 the insides of slotting, this flywheel piece 1403 has other port 1434, and it is used in particular for ccontaining or installs and fixes bolt 1408.

For the annular chamber 1411 that partly will be filled with resisting medium seals up, another Sealing 1436 is set, it is made by the member of a film shape or dish spring shape, and it radially extends in intermediate cavity 1430.

Starting point wheel 1439 of shell construction body 1419 supportings, it is connected with structure 1419 by a welded structure.

With the clutch pack that comprises clutch 1404 and clutch disk 1405, two mass blockes-flywheel 1402+1403 that should describe in Figure 40 constitutes an element of construction A, it can be simple especially and the reasonable manner conduct give assembly unit and transport and install and be screwed on the crankshaft of internal-combustion engine.Be package assembly unit A,, install in the centre under the situation of clutch disk 1405 and interconnect at first with the clutch 1404 and the second flywheel piece 1403.After this, comprise clutch 1404, the following edge element of flywheel piece 1403 and clutch disk 1405 and member 1413 are done axially assembling, on this basis, shell construction body 1419 (it is installed on the outward edge 1423 of clutch housing 1422) just is brought on the outer region that rests on member 1413 and can welds with its (at 1420 places).Before two members 1413 and 1419 are done axially assembling, spring 1410 is placed in the zone 1412 of toroid.This element of construction A is integrated in one bearing 1406 and its (1406) is installed in the portion of extending axially 1415 in addition.In addition, in the through hole 1407 of flange region 1414, given dress or contain fixing bolt 1408 is arranged, and its structure is a socket head screw 1408.Simultaneously, screw 1408 is on the corresponding position of the Lower Half with Figure 40.These screws are that anti-lost territory remains among assembly or the unit A on this position.

Clutch disk 1405 is between the friction surface 1432 of the platen 1428 and the second flywheel piece 1403 and give at the running shaft of a relative bent axle clamping on the position of centering, in addition, also to make the position of perforate 1443 sd sos that is provided with in the clutch disk, promptly in the process that assembly parts A is installed on the internal combustion engine drive axle, can allow a threading tool pass.As can be seen, perforate 1443 is less than the head 1440 of screw 1408, so just guarantees screw 1408 no problems and can not remain among the assembly A with losing.

In dish spring 1427 and in its tongue 1427a zone, also be provided with perforate or export 1444 and be used for passing through of threading tool.This port 1444 can so be provided with, that is, its (port) constitutes the effect of widening or enlarging to the slot that exists between tongue 1427a.Perforate 1444 in dish spring 1427, perforate 1443 in clutch disk 1405 and the perforate in flywheel piece 1,403 1434 axially are being mutual imbrication, and imbrication in such a manner, promptly for unit A location and installation to bent axle and must dispose under through hole 1407 situations asymmetricly, also can be with a setting tool, as an inner hexagon spanner, pass perforate 1444,1427 and 1443 without doubt and send to and snap in the groove of screw 1408 heads 1440.

The complete assemblies A of this form explains with regard to the installation of flywheel to show and has simplified, because saved various working procedure, as other essential clutch disk centering process, the importing of the working procedure centering mandrel of assembling clutch disk, the centering of clutch disk itself is inserted screw and is tightened clutch and taking-up centering mandrel.

Friction clutch 1404 has a controlling device 1445, and it is similar that itself and Fig. 1 to 27 describe, and guarantees a wear compensation effect by a sensor spring 1446 and a regulating ring 1447.

The torque transmitter of describing in Figure 41 1501 has one can make the antitorque opposed platen 1503 that is connected with I. C. engine crankshaft K, fixes a friction clutch 1504 on it under the situation of a clutch disk 1504 of centre installation.This clutch disk 1505 can be installed on the gearbox input shaft that is not shown specifically.

Clutch housing 1522 have one axially extended regional 1523, it is in outside radially and axially surround the friction pad 1529 of platen 1528 and clutch disk 1505.The end portion 1523a in this clamshell shape or tubular housing zone 1523 cover or surround opposed platen 1503 and with this dish 1503 by fixedlying connected at the prominent product 1524 of this district 1523a setting, the product 1524 of dashing forward is entrapped in the groove that is provided with on opposed platen 1504 excircles.But this housing 1522 also can otherwise be connected with opposed platen 1503, and for example by welded structure, by the Placement of bolt or pin, but they equally preferably are provided with diametrically.

The clutch cover shell 1522 of centering has an annular region 1526 of substantially radially extending inward on the exterior contour of opposed platen 1503, settles a dish spring 1527 that plays two arm bar effects on it pivotally.These dish spring 1527 usefulness radially are positioned at the zone of outside to platen 1528 imposed loads, and therefore, friction pad 1529 is axially clamped between opposed platen 1503 and platen 1528.The tongue 1527a that this dish spring 1527 has radially is used for by a piece-rate system operated clutch 1504.Be transmitting torque between platen 1528 and housing 1522, be provided with torque transmitter, it is preferably the structure of blade spring 1521, its end of 1521 usefulness, and the most handy rivet connects 1521a and housing 1522 is fixedly linked, and fixedlys connected with platen 1528 by the rivet connection equally with the other end.Preferably, the connection between platen 1528 and the blade spring element 1521 connect to realize by so-called immersing oneself in (blind) rivet, as at the first half of Figure 40 and as described in the friction pad extension area radially.

Friction clutch 1504 or torque transmitter 1501 have a controlling device 1545, its with Fig. 1 to 27 in the similar fashion described.Guarantee a wear compensation by a sensor spring 1546 and a regulating ring 1547.

In Figure 40 and 41, this can be directly in shell material the opposed rising sloping platform of punching out be structure like this setting, i.e. these sloping platforms, on the sense of rotation of friction clutch, constitute always an air-flow openings (1547a, Figure 41).By the structure setting of this form,,, just can realize an improved clutch cooling action by the air swirl of a forced mode relatively rotating under the friction clutch situation.Particularly, by the regulating ring 1447 of plastics manufacturing or cooled off with this, the thermal force of this ring is reduced significantly at 1547 o'clock.

This friction clutch 1504 or opposed pressing plate 1503 are member 1550 antitorque ground of or camber of spring flexible by, but can axially limitedly be installed in movably on the live axle K.In the present embodiment, structure and its rigidity that this member 1550 is dish types are so definite, promptly, by live axle K on friction clutch 1504, cause axially and swing or flexure vibrations, damped or be reduced on the program by flexible member 1550, can guarantee this moment friction clutch 1504 particularly its controlling device 1545 have the performance of a no problem.That is can be by the member 1550 of axial deformation, make the live axle of clutch unit 1504 relative internal-combustion engines such as bent axle axially and the clutch separation effect of a maximum possible of flexure vibrations realization.Just can avoid according to this, the function of clutch unit 1504 or its controlling device 1545 is affected.There is not above mentioned separation (connection) effect that makes clutch unit 1504 relative bent axle K, then may make wear compensation device 1545 that a undesirable adjusting takes place, and be to cause owing to the quality of these members with because vibration acts on these qualitative acceleration.That is, do not having to filter the member 1550 of vibration also especially under configuration adjustment device 1545 situations, this must be taken in especially by the inertial force that member produced that constitutes controlling device, according to this, the adjustment of a just essential costliness and/or additional device are so that avoid wear compensation device 1545 to carry out an adjusting that is not based on the pad wearing and tearing.

Under torque transmitter 1501 situations of Figure 41, wear compensation device 1545 acts between clutch housing 1522 and the dish spring bullet 1527.But this torque transmitter 1501 also can be equipped the friction clutch among Figure 33 to 39, that is in this friction clutch, and the wear adjustment device is to act on the dish spring and by between the platen of this dish spring imposed load.

This opposed platen 1503 is to connect 1551 and axial elasticities at radially outer by bolt, and disc-shaped member 1550 is fixedly connected.Can also use sunk head rivet without bolt connects and connect, as represent at Figure 40 first half about the situation that the blade spring is fixed on platen 1428.The footpath is upwards in the inside of link position 1550 and be provided with an axial clearance 1552 between disc-shaped component 1550 and opposed platen 1503, and it has been determined between two members 1550 and 1503 and at the amplitude of a maximum axial vibration on axially.By on disc-shaped component 1550, being provided for the upwards bounding means in inside area territory of opposed platen 1503 footpaths, friction clutch 1504 being moved towards the maximum axial of internal-combustion engine live axle K be restricted.But under normal operating conditions, special under the internal-combustion engine situation of good operation, such device just needn't be set.Opposed platen 1503 rings of this annular enclose an axial jut 1553, and it is the part of an annular or disc-shaped component 1554.This disc-shaped member 1554 can be fixedly linked with the zone, radially the inside of resilient disc 1550.Resilient disc 1550 and disc-shaped component 1554 are centerings on the annular projection 1555 of a K; And be connected and fixed with bolt with it and link to each other.Simultaneously, the zone, radially the inside of this disc-shaped component 1550 is axial clamped between the end surfaces 1557 of axle K and annular construction member 1554.

The portion that extends axially 1553 of member 1554 is equipped with zone 1558 radially in its end away from resilient member 1550, moving axially on another is axial limits to friction clutch 1504 or opposed platen 1503 for it.Between zone 1558 and opposed platen 1503 and on stressless resilient member 1550, be provided with an axial clearance 1559.Size such as the slot 1552 of this gap 1559 on axial direction determined similarly.Opposed platen 1503 can in fact seamlessly be installed on the portion of extending axially or the projection 1553 by inner circumferential surface, in order that can guarantee opposed platen 1503 an axial leading is arranged.But, can also be in the interior perimeter surface of opposed platen 1503 with extend axially and be provided with a small gap between the portion 1553 at least, that is under normal operating condition, between these two members, not have contact by the purpose requirement.

According to a flexible program, for the vibration that resilient member 1550 is transmitted suppresses, a vibrational energy cancellation element can be set, this device can connect with a friction link, as described at Figure 42.In the modified embodiment of in Figure 42, describing, a vibration damping equipment 1560 is set, it is between the outer surface of the zone, the inside of opposed platen 1503 and extension part 1553, and this device 1560 can have the ring of waveform to constitute with one in a circumferential direction, and its waveform is a radial arrangement.This ring 1560 is that tensioning is installed diametrically, according to this, for example between the interior perimeter surface of this ring 1560 and opposed platen 1503, just produces friction under the situation that has axial vibration.That is opposed platen 1503 is realized the supporting of a vibration damping on extension part 1553.The ring 1560 of this waveform can separate on its circumference, that is open type.

The resilient member 1550 of this dish type is starting gear 1561 of supporting outside radially.

This disc-shaped component 1550, opposed platen 1503, clutch disk 1505 and friction clutch 1504 constitutes an element of construction, it can be simple especially and reasonable manner give assembling, transport and settle, and be screwedly mounted on the bent axle K of internal-combustion engine.Fixing bolt 1556 of hexagonal screw thread had equally given and having installed in this was shaped as, that is was included in the element of construction and can prevents loss.

Clutch disk 1505 is to be clamped at a relative bent axle rotating shaft to give on the position of centering between platen 1528 and opposed platen 1503, in addition, also want on position of sd so, promptly, the through hole 1562 that in this dish 1505, is provided with, (it is positioned at the inside of the spring cushion of this dish 1505 on radially) in the process that assembly is installed on the K, can allow a threading tool 1563 pass.Also have dish spring 1527, also have the through hole or the opening 1564 that are used to import threading tool 1563 where necessary.The through hole of this dish spring 1527 or opening 1564 should cover mutually with the through hole 1562 of clutch disk 1505, in order that setting tool as a consistent cutter 1563 of interior hexagonal, can snap in the tight helical groove of screw 1556 heads no problem.

Describe as implementing structure in conjunction with other, by using a friction clutch 1504 that has the controlling device 1545 that wearing and tearing compensate to pad at least, just can realize the optimization configuration of a friction clutch, particularly the power storage 1527 that applies the clutch disk tension force be realized the optimization setting.This power storage can so be provided with, that is, and and clamping force essential and that act on clutch disk when its only actually is applied to the torque of transmitting hope.Just can guarantee that by this controlling device 1545 in fact power storage 1527 keeps identical rigging position under the jointing state of clutch unit 1501 and during Complete Service Life.In addition, by the controlling device of the same structure that in clutch unit 1501, is provided with for pad spring 1565, (its separation of 1501 and when engaging in the unit, at least during a part of platen operational stroke, can cause realizing an elimination (reducing) or a foundation (increase) gradually by this unit torque transmitted), just can realize reducing of a Separating force or Separating force curve.That is, by will suitably adjusting, just can determine the Separating force curve of hope by pad spring applied force or power-stroke curve in the controlling device with by power or power-journey curve that power storage (it acts on the platen) applies.Can also make resilient member 1550 according to this, with regard to its for axially-crooked-or the swing vibration reach with regard to the damping property of hope, do the optimization configuration, because effect and the Separating force that reduces are unessential on this resilient member.Like this, essential steering force does not obviously move axially under the situation at clutch unit in order to separate this clutch, can be supported by this member.

The friction clutch 2001 that the clutch pack of describing in Figure 43 has a band housing 2002 with have one and be connected with housing is antitorque, but axially can limited mobile platen 2003.Axially dish spring 2004 is pushed in one of tensioning between platen 2003 and housing 2002, it can turn round around an annular pivoting support 2005 by the housing supporting, and to platen 2003 towards an opposed platen 2006 of fixedlying connected with housing 2002, as imposed load on the direction of a flywheel, according to this, the friction pad 2007 of clutch disk 2008 is clamped between the friction surface of platen 2003 and opposed platen 2006.

Platen 2003 is by doing antitorque the connection at the leaf spring 2009 of circumferencial direction or tangent line sensing with housing 2002.Under the present embodiment situation, clutch disk 2008 has so-called pad spring sector 2010, it is guaranteed under friction clutch 2001 joint situations, there is a progressive torque to increase, wherein, its (2010) can also make the axial force that acts on the friction pad 2007 realize a progressive raising by limited move axially of two friction pads 2007 in opposite direction.But, can also use such clutch disk, at this moment, friction pad 2007 is actually vertically and is installed in rigidly on the supporting disk.

In illustrated embodiment, dish spring 2004 has a ring matrix 2004a who propagates impacting force, from its operation tongue 2004b that radially extends internally out.And this dish spring 2004 is assemblings like this, and it is exerted pressure to platen 2003 with its radially outer zone, and supporting 2005 upsets are changeed in the regional wraparound of available its inner radial.

Rotating support 2005 comprises two pivoting supports 2011,2012, and dish spring 2004 axially is being supported or is being clamped between these two supports.The pivoting support 2011 that is provided with on the face of platen 2003 at dish spring 2004 is in the axial direction facing to the direction application of force of shell 2002.In addition, this revolution part 2011 is parts of the member 2013 of a dish spring or dish spring type, these parts flexibly are bearing on the housing 2002 with its outer edge region 2013a, so the pivoting support 2011 of this inner radial moulding is being pressed and operated dish spring 2004 and also be the application of force on the direction of shell 2002 in the axial direction.The dish spring 2013 that is arranged in the axial direction between platen 2003 and the operation dish spring 2004 has a circle ring area 2013b, radially inwardly extends to tongue 2013c by this regional inward flange, and it has constituted pivoting support 2011.

In order to support the member 2013 of this dish spring type, in illustrated embodiment, between housing 2002 and tongue type trailing arm 2013a, be that socket connection or clamping are arranged.

This dish spring type member or dish spring 2013 constitute as sensing spring, and it produces one at least near constant power on a predetermined work stroke.By this sensing spring 2013 clutch separation power of blocking effect on the tip of the tongue 2004c at least basically, counter-force on the revolution part 2011 always keeps at least near balance being acted at the power that produces on the pivoting support 2011 and sensing dish spring 2013 by Separating force.Separating force should be interpreted as the maximum, force that when friction clutch 2001 operations, acts on the tip of the tongue 2004c or the dish languid 2004c of the portion separated region.

The pivoting support 2012 of case side is bearing on the housing 2002 through a controlling device 2016.This controlling device 2016 has guaranteed: at pivoting support 2011 and 2012 towards the direction of platen 2003 or towards the axial displacement of the direction of opposed platen 2006 time, at pivoting support 2012 and housing 2002 or be not form any undesirable gap at pivoting support 2012 and dish spring 2004.Just guarantee when actuating friction clutch 2001, not produce any undesirable backlash or idle stroke thus, just obtained the perfect operation of best efficient and friction clutch 2001 thus.This pivoting support 2011 and 2012 axial displacement are to occur when the rubbing surface of platen 2003 and opposed platen 2006 and friction lining 2007 axially weares and teares.

This controlling device 2016 comprises the spring pressurization adjusting parts 2017 of a ring-shaped member form, and these parts have one reaching at the rising sloping platform 2018 that axially stretches out that circumferencial direction extends, and it is distributed on the circumference of parts 2017.These adjusting parts 2017 are to be installed in like this in the clutch 2001, that is, make rising sloping platform 2018 shift to 2002a at the bottom of the shell.

This regulating ring 2017 is to apply spring force in a circumferential direction, and regulating on the sense of rotation, also promptly formed the axial displacement of regulating ring 2017 towards platen 2003 directions by the rising of sloping platform 2018 on the opposed sloping platform 2019 of casting in 2002a at the bottom of the shell, this means leave shell zone 2002a radially axially on displacement.

Also to be described in greater detail for other configuration possibility of the automatic regulatory function of revolution part 2005 or controlling device 2016 and controlling device 2016 in conjunction with Fig. 1 to 32.

This clutch unit comprises a compensation device 2020, and it is used for guaranteeing: seamlessly operate the segregating unit of the friction clutch 2001 that is made of dish languid 2004b in the axial direction and move it on a constant stroke 2021.This compensation device 2020 is located between the separator 2022 and the tip of the tongue 2004c that comprises a release bearing.Separator 2022 is enclosed within on the conduit of representing with sketch 2023 and can moves in the axial direction with respect to actuating friction clutch 2001.This conduit 2023 by one not depicted in greater detail driving mechanism shell supporting and surround the driving mechanism driving shaft, on this axle, also can resist and accept clutch disk 2008 rotationally.The required power of separator 2022 axial displacements is obtained by operation equipment 2024, and it utilizes the indignant separator fork that will represent to constitute in this illustrated embodiment, and it similarly is supported on the driving mechanism side.Yet also can use hydraulic pressure or Pneumatic pressure operated separator 2022, also promptly have separator with a pressure medium loaded piston/cylinder unit.

Compensation device 2020 is depicted in Figure 44 and 45 with the size of amplifying, and comprises the adjustment component 2025 of an annular construction member form, and this components list is shown among Figure 46 and Figure 47.This ring-type adjustment component 2025 has two and is radially staggering in the illustrated embodiment, and in the rising sloping platform group 2026,2027 that circumferencial direction extends and rises in the axial direction, they all are distributed on the circumference of parts 2025.As especially represented in Figure 47, the upwards inner rising sloping platform 2026 in footpath staggers at circumferencial direction with respect to the upwards outside rising sloping platform in footpath 2027, and half of approximately stagger sloping platform length or sloping platform part.As from Figure 43 and 44, finding out, regulate its end face of parts 2025 usefulness 2025a and directly be bearing on the tip of the tongue 2004c.These rising sloping platforms 2026,2027 deviate from operation equipment 2004b in the axial direction.This regulates parts 2025 in a circumferential direction by spring-loaded, and adjusting on the sense of rotation, by sloping platform 2026,2027 in Figure 48 and 49 the opposed rising sloping platform 2028 on the supporting ring 2030 of depicted in greater detail, slip on 2029 forms this adjustment ring 25 in an axial displacement on platen 2003 directions, this means that leaving axially going up of separator 2002 produces displacement.

By what can from Figure 48 and 49, find out, the two groups of sloping platforms no matter these opposed rising sloping platform 2028,2029 same formations still stagger diametrically in a circumferential direction each other.This regulates the sloping platform 2026,2027 of parts 2025 and sloping platform 2028,029 aligned with each other the reaching of supporting ring 2030 axially are being engaged with each other.Can guarantee by the sloping platform that staggers in a circumferential direction: between adjustment component 2025 and supporting ring 2030, present perfect entad guiding.As especially appreciable in Fig. 44, two parts 2025 of this balace weight 2020 and 2030 fasten in the axial direction each other, the configuration angle 2031 (Figure 49) of the opposed sloping platform 2028,2029 of supporting ring 2030 is corresponding to the angle 2032 (Figure 47) of the sloping platform 2026,2027 of adjustment component 2025.Supporting ring 2030 can be connected rotationally with housing 2002 is anti-, yet it is axially can the about clutch operating stroke 2021 of limited ground displacement.This axial restraint is to be realized by the radial zone 2033 of supporting ring 2030, and the end is being covered radially on the inner region 2002a by being placed under the jointing state of friction clutch 2001 in this zone.This is that operation equipment 2004b by applying spring force causes by putting.When friction clutch 2001 separated, its travel limits was guaranteed that by a sheet component 2034 it is set on the side of the supporting ring 2030 that deviates from operation equipment 2004b, and can separated device 2022 application of force in diameter region 2035.This sheet component 2034 has a radial zone 2036 equally, and this zone can contact at the lid end radially on the inner region 2002a when friction clutch 2001 separates.

In illustrated embodiment, adjust ring 2025 and supporting ring 2030 by heat-resisting composite, make as heat resistant plastice, it also can additionally be strengthened with fiber.These parts can be with simple mode as manufactured come out of spray casting die thus.

Rising sloping platform 2026,2027 and opposed rising sloping platform 2028,2029 is to constitute like this at circumferencial direction: between these two members 2025 and 2030 windup-degree can be arranged at least, this angle has guaranteed to make in the whole operating life of friction clutch 2001 on the rubbing surface of platen 2003, opposed pressing plate 2006 and friction lining 2007 occurring wear to be readjusted.This adjusts the angle calmly can be in the value scope between 30 ° and 90 ° on the layout of slip rising sloping platform.In Figure 45 75 ° the order of magnitude in illustrated enforcement just with the torsion angle shown in the label 2037.The configuration angle 2031 of sloping platform and opposed sloping platform and 2032 can be in the number range of 6 ° and 14 °, be preferably 8 ° the order of magnitude, wherein, the true angle 2031 of sloping platform and opposed sloping platform and 2032 changes on the radially bearing of trend of these sloping platforms, because must overcome identical height difference for a given torsion angle.The increase sloping platform angle 2031 and 2032 of diameter this means, along with will reduce.

Adjusting the required power that applies at circumferencial direction for parts 2025 realizes by means of force-storing device, it is to be supported on supporting ring 2030 and to be adjusted helical spring 2038 between the position 2025 by what two arcs were arranged in illustrated embodiment, 2039 formations, these helical springs 2038,2039 are bearing in and cover on the 2002 anti-supporting rings 2030 that are rotationally connected, and adjustment ring 2025 is rotated, as long as at this moment because the wearing and tearing of liner make functional unit or the dish languid 2004b of portion axially leave the words of covering end 2002a or separator 2022.As especially can seeing from Figure 45 and 48, these helical springs 2038,2039 are placed in the receiving-member 2040,2041 of the ring 2030 that ditch shape in a circumferential direction or bracket shape extend.As from Figure 44, seeing, in cross section with force-storing device 2038, such receiving-member 2040 that 2039 bung flange matches extends on the half cycle greater than a spring 2038 or 2039 cross sections, and as from Figure 45 and 48, seeing, on the side of operation equipment 2004b, always be provided with a slotted hole 2042,2043 and on the side of the supporting ring 2030 of carrying operation equipment 2004b, always be provided with a slotted hole 2044,2045.Spring 2038,2039 utilizes the face of restriction receiving-member 2040,2041 to be maintained facing to supporting ring 2030 in the axial direction.For helical spring 2038,2039 is penetrated, these fan-shaped receiving-members 2040,2041 respectively have one and wear spring zone 2046,2047, and they have a guidance field radially, and this guidance field is equivalent to the external diameter of helical spring 2038,2039 spirals at least.Wear 2046,2047 tops, spring zone from these, these power storages 2038,2039 can be pushed in the fan-shaped receiving-member 2040,2041 obliquely.After these helical springs that still relaxing 2038,2039 are encased in these fan-shaped receiving-members 2040,2041, again adjustment component 2035 and supporting ring 2030 are combined.On adjustment ring 2025, be provided with axial projection 2048 for this reason, 2049, their while structures are made helical spring 2038,2039 application of force zone or support region, each projection are inserted in a circumferential direction and wear the axial groove zones 2050 then that link to each other, spring zone 2046,2047, in 2051, application of force zone 2048,2049 is touched on the end regions of lax helical spring 2048,2049.Power storage 2038 or 2039 relaxed state can be found out from Figure 45 and represent with 2039a.The other end area supporting of these helical springs 2038,2039 is located at the bottom 2033 of circumferencial direction, among the 2053a at fan-shaped receiving-member 2040,2041.Can make spring 2038,2039 preloads by adjusting reversing between ring 2025 and the supporting ring 2030.After turning over a definite relative torsional angle, promptly turn over greater than wearing spring zone 2046, after 2047 the extension angle, the application of force zone 2048,2049 of adjusting ring 2025 always is on the position of an end regions that surpasses groove 2044,2045 in the axial direction, make adjustment ring 2025 and supporting ring 2030 reciprocally to move, be in contact with one another up to rising sloping platform 2026,2027 and opposed rising sloping platform 2028,2029.Groove 2044,2045 and axial projection 2048,2049 are aimed at each other in this wise, promptly form a kind of kayser connection of axially working between two parts 2025,2030.Axial projection 2048,2049 has a hook-shaped section 2048a at its end regions for this reason, and it is by on the zone that is placed on supporting ring 2030 and radially extends.Utilize once additional corresponding to the reversing relatively of angle 2037 (Figure 45) between these two parts 2025 and 2030, the new state that spring 2038,2039 is compressed to friction clutch 2001 compresses angular length degree 2054 accordingly.When this position, these two parts 2025,2030 can be pinned by a unshowned device.This device for example comprises a configuration blocking element, and it works between these two parts 2025 and 2030, and can be removed after friction clutch 2001 is assembled on the opposed platen 2006, and this compensation device 2020 is played a role.What be used for compensating especially liner wearing and tearing may adjust the torsion angle that the angle is represented with label 2037 corresponding to Figure 45.According to torsion angle 2037, axial projection 2048,2049 is adjusted the end regions that has in the direction with groove 2044,2045 at ring 2025 and is contacted.The depressed position of the corresponding helical spring 2038,2039 in position is represented with label 2038a in Figure 45 therewith.

When the new state of friction clutch 2001, the axial pawl 2026,2027 and 2028,2029 that constitutes rising sloping platform and opposed rising sloping platform is fitted to each other on axial position farthest.This means mutually and need minimum axial arrangement space by the ring of putting 2025 and 2030.

In illustrated embodiment, operational stroke is guaranteed by sheet component 2034 on the detaching direction of friction clutch 2001.According to a unshowned form of implementation, to this required thrust zone, for example be and lid 2002 coefficient thrust zones also can be arranged on separator 2002 sides, or be located on the bearer ring that friction clutch rotates, or be located on the parts that are connected with these parts.The axial restraint of the operational stroke of friction clutch 2001 forms in the axial stop that is used for separator 2022 that also can be located at by at least one on conduit 2023 sides at least one axial direction.

In addition, separator 2022 can directly act on operation equipment 2004b, and between separator 2022 and segregating unit 2024 corresponding compensation device is set.

What conform with purpose is that separator 2022 usefulness do not hinder a precompression of friction clutch 2001 and compensation device 2020 functions to be applied on the direction of operation equipment 2004b.

As appreciable from Figure 44 to 46, on regulating ring 2025, have radially inner protruding 2055, its structure acts on the zone of action of a rotation or braking device, and it can be located on shell 2002 or supporting ring 2030 sides, in order to the locking that rotates on the other hand when needed.This class braking device is provided with when making or assemble friction clutch 2001 and compensation device 2020, and promptly is removed after friction clutch 2001 is assembled on the flying wheel 2006.

The details table of describing in Figure 50 is shown in the enforcement modification of 2020 lower half portions of compensation device shown in Figure 43 and 44.In this modification according to Figure 50, in the jointing state of axial restraint between compensation device 2120 and the housing 2102, be to realize by hook-shaped axially mounting 2133 at clutch, this supporting constitutes one with sheet component 2134.This supporting 2133 is molded over as on the outer rim of the sheet component 2134 of casting die and axially pass and cover 2102.It on the free end of dish spring 2104, this supporting 2133 really has the regional 2133a that extends radially outwardly, it radially catches lid 2102 at it on a side of dish spring 2104.Just guaranteed by this configuration: the axial force that is acted on compensation device 2129 by dish spring 2104 is bearing on the pressure containing part 2034 that is made of sheet material, so that the axial force that is subjected to by compensation device 2120 is greater than the suffered axial force of the compensation device in Figure 44 2020, thrust is that zone 2033 by the supporting ring made from plastics 2030 forms on the latter.When this in addition axial force that acts on compensation device 2020 and 2120 also may appear at transportation, when being the situation of unassembled clutch, because master's dish spring 2004 or 2104 axially is bearing on supporting ring or the plastics compensating unit 2030,2130 by spring-latch when this state.This pressure containing part 2134 that is made by sheet material can be at least have two preferably three or more hook-shaped supportings 2133, and they preferably symmetrically or be evenly distributed on the circumference.The sheet strength of pressure containing part 2134 can be provided with according to the axial force of supporting.Should form rotation inhibiting with pressure containing part 2134 by the ring 2140 that plastics make is connected.With among Figure 44 similarly, this pressure containing part or sheet component 2134 radially outers also have zone 2136, it is seen from circumferencial direction and extends between the hook-shaped supporting 2133, and limits the separation stroke and be used to avoid unallowed super large stroke by the bounding means on shell 2102.

The details of a kind of friction clutch 2201 of representing in Figure 51 has friction clutch 2001 bottom-right structures among the Figure 43 of being similar to basically.The part face of land illustrates clutch housing 2202 in Figure 51, is used for the pivoting support 2205 of dish spring 2204, controlling device 2216 and compensation device 2220.The function of controlling device 2216 and compensation device 2220 points out in the description to Figure 43 to 50 or points out in German patent application P4306505.8 and P4239289.6, and their content is especially in conjunction with in the present invention as a reference.

In enforcement modification, be provided with a rotation locking body 2260 that is used to adjust the adjustment component 2217 of loop type according to Figure 51.

This adjusting or rotate locking body 2260 and guarantee on unassembled friction clutch, adjustment component 2217 has a definite position with respect to other member as shell 2202 especially.Especially can guarantee by this adjustment locking body 2260, making adjusting parts 2217 remain on it when the new state of friction clutch 2201 recalls on the position, promptly in fact also do not carry out on the zero position of any adjusting, though at this moment dish spring 2204 does not also encircle 2217 application of forces to the adjustment in revolution or supporting member 2212 zones.Revolution part is withdrawal in this wise then, and promptly main dish spring 2204 axially is bearing in compensation device by its languid on the friction clutch 2201 on unassembled friction clutch 2201 or when being used to deliver, and can find out in conjunction with Figure 43 and 44 as this.Because the force transducer 2213 of dish spring form is being pressed in this supporting, main dish spring 2204 on the direction of axially leaving shell 2202 or adjustment ring 2217.Just no longer can be guaranteed at axial compression adjustment ring on shell 2202 directions 2217 thus.If do not rotate locking body 2260, ring 2217 will produce mobile.When friction clutch 2201 is assembled on the live axle of an internal-combustion engine, not to have retracted position at the desirable compensation of carrying out for occurring wear on the friction lining that guarantees clutch disk especially for those.Clearly express the position of each member in Figure 51, it is equivalent to be assemblied in a friction clutch on the flywheel.Dotted line is represented the position of dish spring 2204 and sensing spring 2213 in the new clutch of not assembled.As can be seen, in the unassembled state of clutch 2201, between adjustment component 2217 or ring-shaped bearing piece 2212 and cup spring 2204, have an axial distance or space.

In addition, the adjustment locking engagement 2260 that is used for regulating device 2216 for the transport point setting of friction clutch 2201 has a locking component 2261 at least, it does not have with respect to shell 2202 during the jointing state at the friction clutch 2201 that assembles in the unassembled state of friction clutch 2201 or when needing at least and is keeping rotationally, and with shell 2202 actings in conjunction, be used to make adjustment component 2217 to rotate lockings.This locking component 2261, as in Figure 52, representing, have at each arm 2262 that radially extends, its radial outer end is fixedly connected with adjusting ring 2217, and its radial inner end is clamped between the bounding means 2233 and shell 2202 that shell 2202 sides towards dish spring 2204 are provided with regularly.Make adjustment component 2217 form being connected of transmission power thus with shell 2202.This arm 2262 can be to resemble also radially inwardly being connected to each other through an annular region 2263 of leaf spring ground formation.Arm 2262 screws with adjustment component 2217 usefulness screws in illustrated embodiment.Yet arm 2262 also can be riveted with adjustment component, or has the whole zone that is embedded in the plastics that constitute these parts in order to be connected with adjustment component 2217.

Compensation device 2220 and limit stops 2233 constitutes a braking or a clutch that is used to regulate parts 2217 with the axial clamping zone of shell 2202 and locking component 2261, and it works when actuating friction clutch 2201 not.

When clutch separation, the braking of this locking component 2261 or lapping plate 2262 or clamping action are gone to disappear, so that can regulate this adjustment component when needed or adjust ring 2217.

Advantageously, when locking component 2261 or the leaf-spring-like bridge piece that constitutes these parts axially have little spring rate or elastic stiffness, face has big relatively elastic stiffness or harder situation in a circumferential direction.

In the form of implementation that represent at Figure 53 adjusts ring 2317, axial elasticity bridge piece 2362 be directly plastic-blasting on plastic hoop 2317.This bridge piece 2362 can be used mode similar shown in Figure 52, radially inwardly is connected by a circular annular region.

Clutch unit of describing in Figure 54 A to Figure 55 and friction clutch 2401 have one by plate lid 2402 shells that constitute, one with shell anti-be rotationally connected but axially can be spacing mobile platen 2403 and one at this dish and cover the dish-shaped stage clip 2404 of 2402 intermediate pressurised.This dish stage clip 2404 is being supported as double armed lever on shell 2402 opposites, and it is remained in the single-revolution supporting 2405 rotationally by turning reaching simultaneously.These dish spring 2404 usefulness facing to annular pivoting support 2405 radial outer end zones on the direction of the friction lining 2407 of clutch disk 2408 that can be clamped between a platen 2403 and the flywheel to platen 2403 application of forces.Transmission of torque between platen 2403 and lid 2402 realizes that through leaf spring 2409 this leaf spring can be by friction lining 2407 preloads on the lifting direction of platen 2403.

Dish spring 2404 has a ring-type matrix 2404a, and sets out thus radially to the tongue 2404b of interior orientation.

This swinging mounting 2405 comprises two pivoting supports 2411,2412, and dish spring 2404 axially is being supported or is being clamped in the middle of these two supportings.This pivoting support 2411 and 2412 has similar layout and structure with the pivoting support 2011 and 2012 that combines Figure 43 description, and has identical functions.Relevantly act on the parts of pivoting support 2411,2412 and the automatic corrective action of pivoting support 2405 is pointed out by the description to Figure 43 and Fig. 1 to 32.

The segregating unit of the friction clutch 2401 that is made of the dish languid 2404b of portion can change the gradient of dish spring 2404 thus by a separator 2422 axial operation.This separator 2422 can have a compensation device 2420 with to combine the described separator of Figure 43 to 49 similar.And in the clutch release system with self-regulating separation support, the compensation device 2420 of this class is unwanted.Separator 2422 is connected with the separation support ring that detours with clutch 2401 in separation process at least in such piece-rate system.

For fear of the big separation stroke of the unallowed clutch release assembly that constitutes by dish spring 2404b, the dish languid 2404b of portion is provided with stroke restricting means 2436 on clutch 2401 or shell 2402.The trip restricting means 2436 utilizes the axially mounting of the dish languid 2404b of portion and utilizes axially the cutting of Separating force that acts on the separator 2422 kept off oscillating stroke or the angle of oscillation that has limited dish spring 2404.

In illustrated embodiment, the trip restricting means 2436 is made of the annular stop zone 2436 that is constituted by the radially inner side section of lid 2402, and the tip of the tongue 2404c contacts with stopper area in a predetermined axial stroke 2421 backs.This annular stop zone 2436 is to constitute like this: it at least almost is positioned on the separation diameter of dish languid portion, just this diameter, separator 2422 contacts with dish spring 2404b formation on this diameter.This thrust zone 2436 axially is arranged between spring-latch 2404b or spring the tip of the tongue 2404c and the clutch disk 2408.

This annular thrust zone 2436 is connected with lid 2402a by muscle or the web 2437 that radially stretches.As seeing, in illustrated embodiment, has the such web of the six roots of sensation from Figure 55.Also three such webs can only be set for some applicable cases.In the clutch embodiment of the big especially Separating force of needs, can use more web, for example be provided with nine.

These webs 2437 radially extend internally and tilt towards the direction of platen 2403 or clutch disk 2408 in the axial direction from lid end 2402b or from lid 2402a.Thrust zone 2436 axially is displaced to respect to lid end 2402b and covers in the chamber.Spring-latch 2404b is passed in the hole 2438 that forms between the lid 2402a of annular thrust zone 2436 radial outsides and the connecting tendon 2437 and stretches out.In illustrated embodiment, these dish languids 2404b of portion radially inwardly forms bending or perpendicular coming by its part area of length in the direction that axial anti-muscle 2437 extends for this reason.By Figure 55 as can be seen, these dish languids 2404b of portion constitutes three groups, and each assembly has a hole or mouth 2438.In the middle of each group, always be provided with a seam 2439 and be used to receive muscle 2437.The so each other calibrating position of these seams 2439 and muscle 2437 promptly makes dish spring 2404 to swing perfectly.

The dish languid 2404b of portion passes hole 2438 and realizes when friction clutch 2401 assemblings.For this reason, dish spring 2404 is in relaxed state, and it dots in Figure 54 A, and it has an internal diameter 2440 in the zone of the tip of the tongue 2404c, and this internal diameter is greater than the external diameter 2441 in annular thrust zone 2436.This dish spring 2404 thus, available its dish languid 2404b of portion axially passes the hole of covering on 2,402 2438 in relaxed state fully at least.When friction clutch 2401 assembling or at the latest when friction clutch 2401 was installed, when for example being installed on the flywheel, this dish spring 2404 was swung, and the internal diameter 2440 that is limited by the dish languid 2404b of portion is diminished.On the strigil that is installed on the flywheel, dish spring 2404 has its working position, and the tip of the tongue 2404c defines an internal diameter 2442 less than thrust zone 2436 external diameters 2441.This dish spring 2404 can remain on the shell so rotationally and tongue 2404a constitutes like this: after returning revolution stroke 2421, the internal diameter of being determined by tongue is still less than the external diameter in thrust zone 2436.

The maximum possible operational stroke 2421 of axial limiting is such sizing: when the maximum that reaches liner 2407 allows wear extent, clutch 2401 should have at least still complete given separation stroke, and also promptly perfect separation is necessary to the trip for the consummating function of clutch 2401.The automatic compensation of clutch 2401 or liner wearing and tearing guarantees that the sensing spring 2413 of usefulness and regulating device 2416 are to be provided with like this in the friction clutch: when the new state of friction clutch 2401, stroke 2421 fully by the time pivoting support 2405 the axial adjustment of mistake can not appear for itself.

Below illustrate and discuss cooperatively interacting between thrust zone 2436 and the dish languid 2404b of portion by means of the data example.

The separation stroke of above-mentioned friction clutch 2401 is 8.4 to 10mm considering to exist under the situation of tolerance.Clutch 2401 is like this designs, and to surpass 14mm just may be that the axial mistuning of pivoting support 2405 is whole when separating stroke when its new state.Stop member 2436 is such formation and location: form the zone that contacts with stop member 2436 when the new state of friction clutch, promptly the tip of the tongue 2404c can return the axial stroke of 12.5mm.When dish languid portion touched bounding means 2436 and obtains maximum separation power, lid also can be flexibly moves about 0.5mm in axially, and therefore the axial stroke of maximum can be 13mm.

Suppose that the greatest wear amount that can allow is 3mm on liner 2407, then on the direction of clutch disk, moving about 3mm by the axial displacement of its pivoting support 2405 at dish spring on the useful life period of friction clutch 2401.Therefore the separation stroke 2421 of maximum possible reduces to about 10mm from about 13mm, so that clutch uses the working life at the end also to be in the separation stroke tolerance 8.4 of requirement to 10mm at it.

In illustrated embodiment, stop member 2436 constitutes one with lid 2402.This thrust piece also can constitute with the lid 2402 independent parts that are connected by one.Simultaneously web 2437 also can by independent parts or with the stop member 2436 that constitutes as member separately are one.

In the clutch unit shown in Figure 54 A and 55 2401, also be provided with parts or device, it is when clutch unit 2401 work, and being taken in the part area of speed range at least improves the axially mounting power of dish spring 2404 when clutch unit 2401 effectively rotates.Improve and can avoid by this supporting force: produce unallowed adjustment when the disturbing factor in definite rotating speed interval makes clutch unit 2401 operations owing to appear at least, this adjustment is based on and turns round the sensor 2413 of part 2411 a coefficient sensing spring form records undesirable, the non-axial deviation that is caused by the wearing and tearing of friction lining 2407 or descend and forms.

In Figure 54 A, be provided with the device 2450 relevant that to act on revolution part 2411 axial force and be provided with in order to improve with rotating speed or centrifugal force.Should the device 2450 relevant be by constituting at tongue 2450 distortion of the periphery of sensing dish spring 2413 and that raise towards lid 2402 directions with centrifugal force.As seeing from Figure 54 B, the sensing spring 2413 of dish spring shape has the ligule carriage 2413a that extends radially outwardly, and it axially is bearing in and covers on 2402 as seeing from Figure 54 A and 55.At carriage 2413a and to support between its axial region 2451 of lid 2402 be a kind of bayonet coupling or latch 2452.This bayonet coupling is to constitute like this: by the axial junction of sensing spring 2413 and shell 2402 and by the relatively rotating of appearance subsequently between these two parts, carriage 2413a axially is positioned on the support region 2451 of shell 2402.At sensing spring 2413 and covered for 2402 whens assembling and make before rotating these two parts sensing spring 2413 at first stressed and its power is unloaded, carriage 2413a is bearing in precompression covers on 2402 on axial elasticity ground.As seeing, radially be provided with a tongue 2450 on the both sides of carriage 2413a at one from Figure 54 B.2401 when rotating in the friction clutch unit, because the centrifugal force that acts on the tongue 2450 will produce a power, it be superimposed upon since precompression make sensing spring 2413 power on, the supporting force of operation dish spring 2404 in pivoting support 2411 zones is strengthened.This increases along with the increasing of rotating speed by the power that is attached on the pivoting support 2411 that tongue 2450 produces.Yet the increase of this power is subjected to such restriction, promptly make it be bearing in distortion or revolution on the shell 2402 radially outwardly, so that the additional support power that is produced by the device relevant with centrifugal force 2450 in the scope of pivoting support 2411 no longer or does not in fact continue to increase since a definite revolution level because thereon centrifugal force of effect will make tongue 2450 produce.

When axial force relation between consideration pivoting support 2411 and dish spring 2404 or equilibrium of forces, also should consider the torque transmitter 2409 of leaf spring form.The torque transmitter 2409 of this leaf spring form can be applied in precompression between shell 2402 and platen 2403, so that this platen 2403 axially is being under pressure facing to dish spring 240 by torque transmitter 2409 on the whole duration of work of clutch unit 2401.Therefore oppose mutually by the axial force of torque transmitter 2409 generations and the active force of 2404 pairs of platens 2403 of dish spring, and act on the axial force addition of dish spring 2404, and these two power axial separation force of resistant function on the tip of the tongue 2404c also at sensing spring 2413.Therefore on the clutch unit 2401 that does not rotate, the real sensor power that makes 2404 displacements of dish spring is by making a concerted effort of producing of torque transmitter 2409 and sensing spring 2413 and acts on the dish spring 2404.When clutch unit 2401 rotated, this also need be superimposed with the power relevant with rotating speed or centrifugal force that is produced by tongue 2450 with joint efforts.

Has one for example in the situation of the clutch disk 2408 of the device 2453 of packing spring form, when actuating friction clutch unit 2401, guaranteed to be bearing on the device 2450 at this device 2453 on the part area of platen 2403 lifting travels by clutch disk 2408 carry-over moments with rising gradually or descend gradually, until passing through platen 2403, the axially mountings that dish spring 2404 is adjusted the adjustment component 2417 of loop types relatively make till friction lining 2407 or clutch disk 2408 releases.Guaranteed thus at least almost when friction lining 2407 discharges, to adjust ring 2471 and axially to keep tensioning, and do not produce any adjustment thus at dish spring 2404 and shell or between covering 2402.When clutch unit 2401 separation, when platen 2403 lifts from liner 2407, when clutch unit does not have tongue 2450, only by making a concerted effort that leaf-spring-like torque transmitter 2409 and sensing dish spring 2413 produce as the axial pressure power of main dish spring 2404.Sensor force that should be synthetic is opposite with the Separating force effect on being delivered to the tip of the tongue 2404c.At certain rotary speed area during especially at higher electromotor velocity, may occur because the vibration that motor causes, this vibration causes the axial vibration of platen 2403 again.When platen 2403 axial vibrations, this platen 2403 may rise from main dish spring or dish spring 2404 in short-term, synthetic sensing power is descended in short-term, because at this moment the axial force that is produced by the torque transmitter 2409 of leaf spring form no longer acts on the dish spring 2404.This just causes, device 2416 is reached adjust and neededly concern disturbed in dish spring 2404 or the Separating force that is applied to it and power between the synthetic supporting force that acts on this dish spring 2404, and be reduced in the axially mounting power that acts under the working state of this clutch unit 2401 on the dish spring 2404, make this clutch produce too early or undesirable adjustment thus, and move the operation point that therefore makes dish spring 2404 towards the minimum value direction of disc spring force.During this external certain motor working state, especially when higher motor speed, extra high running shaft circular acceleration may appear, this can produce the peripheral force that causes owing to the inertia of adjusting ring 2417, with owing to act on the adjustment sloping platform of adjusting between ring 2417 and the shell 2,402 2418,2419 make this peripheral force can produce the axial component that acts on the dish spring 2404, and this component and total sensing power are antiparallel, similarly can produce undesirable adjustment thus.Also may make rising sloping platform 2418 owing to vibration occurs, the friction engagement that exists between 2419 weakens, so that become big, help to occur undesirable adjustment thus equally by acting on the Regulation spring 2417a that adjusts on the ring 2417 axial force that produce and that act on the dish spring 2404 in a circumferential direction.

For the above-mentioned shortcoming to the clutch unit 2401 that do not have to be provided with the bearing device 2450 relevant with centrifugal force overcomes, in the embodiment shown in Figure 54 A to 55, be provided with the tongue relevant 2450 with centrifugal force.This device 2450 relevant with centrifugal force compensated the perturbed force relevant with rotating speed, its supporting force of can generation rising relatively with rotating speed or centrifugal force simultaneously, and the power of this power and sensing spring 2411 generations walks abreast.

Should device relevant can constitute in this wise with centrifugal force, promptly for the liner wearing and tearing required be adjusted in the clutch unit 2401 only in state of rest or at clutch unit 2401 very little rotating speeds the time just may carry out.Like this, when clutch unit 2401 rotates or surpass in the time of the rotating speed of threshold vibration to occur, can make regulator 2016 actual being lockable.

In the embodiment of the friction clutch shown in Figure 56 2501, sensing spring 2513 is arranged in the inner radial of dish spring pivoting support 2505.The tongue 2513b that this sensing spring 2513 has a ring-type matrix 2513a and extended radially inwardly out by this housing.Sensing spring is bearing on the annular thrust zone 2536 by this tongue 2513b, and this zone 2536 and annular thrust zone 2436 according to Figure 54 and 55 have similarly to be arranged and constitute.This sensing spring tongue 2513b is bearing on the thrust zone 2536 on the side of dish languid point 2504c.2513a has tongue 2513c equally at this matrix of radial outside, and it leans against and is used on the dish spring 2504 at this dish spring of axially mounting.

Sensing spring 2513 can be assembled into like this and cover on 2502, even it is out of shape in the pressurized direction upper conically, till the external diameter 2541 of internal diameter 2540 greater than stopper area 2536 that is limited by interior tongue 2513b.Can make supporting tongue 2513b pass the hole of covering on 2,502 2538 thus, its perforation means is similar with tongue 2404b and hole 2438 described modes in combining Figure 54 and 55.After tongue 2513b is passed hole 2538, make sensing spring 2513 lax, the inner end region of tongue 2513b is moved on the less diameter, and contact with 2536 formation of thrust zone.

Another kind of possibility is: cover on 2502 for sensing spring 2513 is assembled into, at least in the part area of tongue 2513b axially be bent upwards towards the direction of covering 2502 so that its internal diameter 2540 is defined greater than the external diameter in thrust zone 2536.After sensing spring or tongue 2513b passed the hole 2538 of lid, this tongue 2513b replication in this wise came, and promptly its radially inner region contacts with 2536 formation of thrust zone with certain precompression.By flexural spring, tongue 2513b will be turned back on the position that is stretched fully the figure from the plastic deformation of the dotted line position shown in Figure 56 by dish spring material.In order to make the 2513 moulding distortion of sensing spring tongue, can make on its tongue 2504b or the tip of the tongue 2504c that axially is bearing in dish spring 2504.Bending operation for tongue 2513b can use a kind of instrument, and this instrument supports on the tongue 2504b of dish type operating spring 2504 from the top, and from the below to sensing spring tongue 2513 application of forces, this power puts on tongue 2513b approximately with on the diameter region that is bent.

Thrust zone 2436 or 2536 advantages that have that restriction dish spring 2404 or 2504 separates stroke or angle of revolution are: they can be integral with corresponding clutch 2401 or 2501, and act in the zone of dish languid 2404b or 2504b, can guarantee thus at dish languid 2404b, 2504b touches thrust position 2436, in the time of on 2536, the dish languid can indeformable or only be footy distortion in the axial direction.Can guarantee also that thus dish languid 2404b, 2504b itself can be on itself and the corresponding position of friction clutch 2401,2501 separated states form with a member of clutch disk 2408 yet and contact.In Figure 54, dish spring 2404 dots and is marked with label 2450 with the corresponding position of clutch separation state.Also can avoid thus: dish languid 2404b forms contact with the clutch disk 2408 that rotates relative to this clutch 2401 or slides when friction clutch 2401 separated states.

In according to the embodiment shown in Figure 54 to 56,, be provided with thrust zone 2436,2536 in the zone of 2504c at dish languid point 2404c.These thrusts zone but other structure can be arranged also and with respect to interior the tip of the tongue 2404c, the 2405c radially outward staggers.Yet in a kind of like this configuration, also be satisfactory like this, promptly at the tip of the tongue 2404c, 2405c and the lever arm that exists between the thrust position of radial outer end are selected in this wise, so that dish languid 2404b, 2505b can not produce unallowable bending owing to acting on the Separating force on it and the supporting of stopper area.

May produce described excess or the unallowed big separation stroke that acts on the clutch operating device by this piece-rate system or operation system, this clutch operating device is made of the dish languid in diagram or described embodiment's form.This operation system generally includes: a separation support, and it acts on the operation equipment of friction clutch; An operating device for example is a clutch riding boogie board; And a power that is provided with between separating support and operating device is transmitted circuit.This power is transmitted circuit can be provided with a reception cylinder and a transmission cylinder.Under the situation of piece-rate system, may cause the separation stroke that surpasses the normal separation stroke in this wise with a transmission cylinder and a reception cylinder, promptly the reception cylinder can not be returned fast enough owing to once engaging fast of friction clutch reaches to separate again, it does not reach final position in other words, though so that reception cylinder itself returns one and the corresponding stroke of normal separation stroke when a back to back in short-term clutch separates again, but then produced a synthetic separation stroke for clutch, it be equivalent to normal separation stroke and uncompleted residue return stroke and.Make friction clutch produce a synthetic operational stroke thus, it has surpassed the maximum separation stroke that allows of predetermined clutch significantly.This means that the overtravel storage level that is used to operate that is provided with also may be exceeded on a friction clutch.

Utilization can be avoided unallowed big separation stroke or overtravel when friction clutch is operated according to measure of the present invention or thrust terminator 2036,2436,2536, and it can also guarantee the required and set normal separation stroke at the clutch duration of work.

According to the present invention, especially have at clutch on the clutch of regulator of the friction lining wearing and tearing that compensate clutch disk at least, at least one thrust terminator in the clutch operating path is set very commonly, and it has avoided the overtravel of clutch operating device when operated clutch.This thrust terminator for example can limit the separation stroke of separating support or the revolution stroke of dish spring.Yet such thrust terminator also can be arranged on the other position.The operational stroke of friction clutch can be limited in addition on the definite steady state value, simultaneously also can or detaching direction on or a definite spacing or thrust terminator is set on the direction of engagement.

This snubber can be located in the zone of separation support with favourable mode, because the dish spring at operation equipment such as friction clutch reaches the tolerance chain between the member of determining stroke limit less in this zone.

Under situation with such snubber or thrust terminator, when separating will towards one in fact the snubber of rigidity advance, this parts, the especially over-stress of piece-rate system parts can occur, and also is undesirable on the operation system stepping on as the pin of operator.Therefore according to another structure of the present invention, but in the courses of action of friction clutch, be provided with the device of pressure in the device of a flexible or elastic telescopic and/or the restriction piece-rate system, wherein this device has a prestressing force or needs minimal deformation power or breaking force, and these power are larger than at least and are used for required maximum, force of operated clutch and required pressure maximum.Just guaranteed that thus the clutch riding boogie board can continue to step down when thrust terminator works, or operating motor can make once, and motion proceeds on the definite position.This regulating device that is provided with in the courses of action of friction clutch can be arranged between clutch operating device and the separation support or be provided with separation support with lock out operation device such as clutch riding boogie board or separate between the motor.

In Figure 57, described a piece-rate system 2601, wherein expressed and be used to limit the various of maximum, force that act on clutch operating device 2604 and/or the clutch housing 2602 by separation support 2622 and may arrange.Be provided with an axial thrust device 2636 in Figure 57, it contacts with shell 2602 formation after stroke is determined in separation support 2622 walkings one, and it is similar with the thrust terminator 2036 described situations in combining Figure 43 and 44.Yet the spacing of this separation stroke also can be realized with other form or method, for example be in conjunction with the described form of Figure 54 to 56.This piece-rate system 2601 has one and sends cylinder 2650 and a reception cylinder 2651, and they are connected by a conduit 2652.The piston 2653 that receives cylinder 2651 is supporting and is separating a part 2622, and can axially carry out displacement in a shell 2654.Pressure chamber 2655 supplies with hydraulic medium such as oil via conduit 2652.Oil cylinder unit 2650 has a shell 2656, and it has constituted the pressure chamber 2658 of a variable volume with set piston 2657 therein.This pressure chamber 2658 is connected with pressure chamber 2655 via conduit 2652.In pressure chamber 2658, be provided with a Returnning spring 2659 that is used for piston 2657.Piston 2657 is by a clutch riding boogie board or operation motor, for example axially displacement of motor or pump.The pressure medium loop of this piece-rate system 2601 is connected with a pressure medium container 2660.Preferred mode is that this transmission oil cylinder 2650 directly is connected with pressure medium container 2660 by a conduit 2661.

For the clutch operating power of restriction on segregating unit 2604 and/or shell 2602, in the embodiment of Figure 57, at least be provided with a device in the pressure medium loop of this piece-rate system 2601, it can be with the pressure limit that produces in the pressure medium loop when the actuating friction clutch on a definite value.This device is made of at least one pressure-limit valve in the embodiment shown in Figure 57.In Figure 57, describe a kind of like this difference of pressure limit valve and arranged possibility.A pressure limit valve 2662 so for example can be arranged in the conduit system 2652 and be provided with a return conduit 2663 that turns back to pressure medium container 2660.Replace pressure limit valve 2662 yet a pressure limit valve 2664 also can be set, it is bearing on the shell 2654 or is integral it with this shell and is connected with pressure chamber 2655 and is connected with pressure medium container 2660 via a return conduit 2665.

Represented also that in Figure 57 another is used for the layout possibility of pressure limit valve 2666.This pressure limit valve 2665 is connected and can be bearing on the shell 2656 or with it with the pressure chamber 2658 that sends oil cylinder and is integral.This pressure limit valve 2666 also has a return conduit that turns back to pressure medium container 2660 in addition.This pressure limit valve 2666 has the conduit of itself for this reason, or also can be connected with conduit 2661.

Be used for arranging that the another kind of possibility of pressure-limit valve 2667 is: this valve is made to one at the piston 2657 that sends oil cylinder 2650.This valve 2667 is arranged to be connected with pressure medium container 2660 or be connected with an intermediate store at least at its depressurised side equally.

Also a liquid memory can be set in the pressure medium loop, it is used for limiting the pressure maximum that piece-rate system occurs, simultaneously it works the storage of back by pressure medium to system decompression limiting the thrust terminator that separates stroke, and in fact works as buffer or spring storage thus.

In the clutch unit shown in Figure 58 2701, similar with the situation that the figure that combines the front describes, have in order to automatic compensation and appear at a regulating device 2716 that weares and teares on the friction lining of clutch disk 2708.In this illustrated embodiment, the theory structure of this controlling device 2716 and working method are corresponding with the regulating device in Figure 54 and 55.This adjustment component or adjustment ring 2717 have contact area or thrust zone 2770, and it can interact with dish spring 2704 when the separation process of clutch unit 2701.Thrust zone 2770 is to do like this with respect to the axial positioned opposite with the zone 2771 of its coefficient dish spring 2704: this dish spring zone 2771 in separation process be at least indirect, preferably directly axially mounting adjust ring 2717 with contact area 2770 on.This reverse supporting preferably realizes when reaching the given separation stroke 2772 that slightly surpasses dish spring 2704 in the tip of the tongue 2704c zone or corresponding angle of revolution at least greatly.The phenomenon that this summary surpasses given separation stroke 2772 may be because the mistuning joint or the non-accurate adjusting of piece-rate system cause.Utilization axially mounting dish spring 2704 on contact area 2770 has just guaranteed to adjust ring 2717 and has prevented undesirable rotation.In fact this dish spring 2704 works to exchange the domain 2717 brakings when being scheduled to separate stroke 2772 above one.

In this illustrated embodiment, this contact area or thrust zone 2770 are that the annular portions 2773 by moulding on the ring 2714 of pivoting support 2705 radial outsides constitute.Also can adopt a plurality of carriages that on circumference, distribute 2773 to replace annular radial protrusion.In this illustrated embodiment, this projection or carriage 2773 extend to the outer rim of dish spring 2704 always.In case reached predetermined separation stroke 2772, dish spring 2604 just is bearing on the thrust zone 2770 of adjusting ring 2717 with its exterior domain 2771.Surpassing predeterminedly when separating stroke 2772, it is big that the swing diameter of dish spring 2704 becomes, because this diameter is displaced on the zone 2771 and the contact diameter between the thrust zone 2770 of dish spring 2704 from the diameter of pivoting support 2705.Required Separating force diminishes in the tip of the tongue 2704c zone because this displacement also makes, because the lever ratio of dish spring changes to i+1 by i, and because in fact turn round after surpassing stroke 2772 to separating the dish spring of stroke 2772 as single-arm lever as the double-arm lever supporting from beginning.The direction that also can guarantee to make dish spring 2704 to utilize axially synthetic supporting force that other sensor spring 2713 and leaf spring 2709 produce or loading force to be pressed towards shell 2704 or adjust ring 2717 of reducing by Separating force.Dish spring 2704 also can not be integrally axially to remove from adjusting ring 2717 or covering 2702.After surpassing predetermined separation stroke 2772, sensing spring 2713 is resiliently deformable axially, and owing to the dish spring rises from adjusting ring 2717 in the zone of pivoting support 2705 then.

This projection or carriage 2773 can be with favourable mode plastic-blasting on the adjustment rings of being made by plastics 2770.The maximum, force of axial action on carriage 2773 is poor with to the axial sensing spring power of dish spring 2704 or supporting force of minimum separation power in the dish languid 2704c zone, and this supporting force is produced by sensing spring 2713 and plate spring component 2709.This carriage 2773 is to constitute like this, does not have the distortion of essence when promptly it resists this maximum, force.

Another substantial advantage is: the actual maintenance of the axial ascending amount of pressing plate 2703 is constant, and thus when overtravel 2772, the axial force that is acted on main dish spring 2704 by leaf spring 2709 no longer descends.Because the power that is produced by leaf spring 2709 is the part of synthetic sensing power, because the Security that the residual pressure that this leaf spring keeps has increased the friction clutch overtravel.For example in the scope of the tip of the tongue 2704c, reaching about overtravel of 0.5 to 2mm, the function that does not hinder regulating device 2716 in the car clutch thus.

Pressing plate 2703 rising quantitative limitations also can be implemented, at this moment surpass one predetermined when separating stroke pressing plate 2703 axially mountings on sensing spring 2713.Can corresponding moulding be set at sensing spring 2713 and/or on pressing plate 2703 to this, as pawl, projection or analog.

Yet a kind of friction clutch 3001 as Figure 59 to 62 configuration have a shell 3002 and one and this shell do not have be rotationally connected axially can spacing mobile platen 3003.The dish spring 3004 that an axial tensioning is arranged between platen 3003 and the shell 3002 as plate lid formation, this dish spring with its radially exterior domain towards the opposed pressing plate 3006 of fixedlying connected with shell 3002 for example on the direction of flywheel to platen 3003 application of forces, and with its radially interior area supporting on ring support 3005 by the lid supporting.In illustrated embodiment, this support 3005 is made of a metal loop.When 3004 revolutions of actuating friction clutch or dish spring, this dish spring 3004 that works as double-arm lever is round ring support 3005 upsets, also promptly is bearing on the ring support 3005 along with its inclination changes.By the axial force that in the clutch state, applies the friction lining 3007 of clutch disk 3008 is clamped between platen 3003 and the opposed pressing plate 3006 by dish spring 3004.Operation dish spring 3004 is carried on the face of swinging mounting 3005 by power storage 3009 application of forces of a precompression dish spring form at it, and it axially is pressed between operation dish spring 3004 and the shell 3002.Preferably quantitative in this wise to this by the axial force that this dish spring 3009 applies, promptly this power is greater than being used for the required maximum separation power of cut-off clutch 3001, and the latter acts on the top 3010 of dish languid 3011 in order to actuating friction clutch 3001.Dish languid 3011 carries out the transition on the dish spring matrix 3012 of annular resilient with known manner.In this illustrated embodiment, dish-like support spring 3009 on the radial height of platen convex portion 3013 to operation dish spring 3004 application of forces, so that by supporting dish spring 3009 countertorque is delivered in the dish spring 3004, it is opposite with the moment direction that is produced by the dish spring.Be applied to the axial force of convex portion 3013 or platen 3003 less than the power that in fact obtains by dish spring 3004 thus by dish spring 3004.When 3004 designs of dish spring, must consider; Platen 3003 is applied power effectively for this reason, and this power can guarantee the transmission of torque capacity that friction clutch 3001 is enough.This supporting dish spring 3009 has at each tongue 3009a of radially inner side towards dish spring 3004 direction axial bendings, and it extends between each platen convex portion 3013 from circumferencial direction.This dish spring 3009 can be connected with lid 3002 with the bayonet socket interlocking.The annular matrix that for this reason supports dish spring 3009 has radially outward extension 3009b, and it axially is bearing on the zone of shell 3002 respective configuration.

In order to produce the bayonet socket interlocking between supporting dish spring 3009 and shell 3002, dish spring 3009 is subjected to precompression at first in the axial direction, so that its radially outer zone or carriage 3009b axially are placed on the support region 3002b of shell 3002.Subsequently, by relative accordingly the reversing between dish spring type member 3009 and the shell 3002, carriage 3009b is axially formed with support region 3002b contact.Also can be at the support region 3002b of shell-side by the die castings that in the axial region of shell 3002b, forms or by the ligule otch, after putting into or make dish spring parts 3009 pressurizeds, be pressed in by material deformation these parts 3009 outer edge area below form.Also can adopt and be fixed on the optional feature that covers.

Supporting dish spring 3009 also can constitute like this: it radially operation dish spring 3004 than interior support, at this moment particularly advantageous to some applicable cases is cover side bearing or support on 3005 the height when this supporting is arranged on, also marking with label 3014 just as shown in Figure 59.Under the situation of supporting like this, can not form countertorque to dish spring 3004 because of dish spring 3004 pressure reduce by dish spring 3009.

The leaf spring 3015 that platen 3003 extends by circumferencial direction or tangent direction forms anti-being connected of rotating with shell 3002.Clutch disk 3008 has so-called packing spring section 3016 in this illustrated embodiment, it guarantees that torque forms gradually when clutch 3001 engages, pass through the displacement of the axial limiting of these two friction linings 3007 simultaneously, the axial force that acts on the friction lining 3007 is increased gradually.When friction clutch 3001 separates, transmitting torque decline gradually will be realized in a similar manner.Also can adopt this clutch disk relatively with friction clutch of the present invention, wherein friction lining 3007 is actually rigidly and affacts on the supporting disk.

Can guarantee that by the supporting dish spring 3009 that acts on operation dish spring 3004 dish spring 3004 touches in this supporting by the application of force and with a definite axial force facing to cover side bearing 3005 on the normal angle of revolution of the normal separation stroke of friction clutch 3001 or dish spring 3004.

The parts of dish spring form or dish spring 3009 best structures are made sensing spring, and it produces on a definite working stroke and is similar to constant power at least substantially.Can obtain the clutch separation power that acts on the tip of the tongue 3010 at least in fact by this spring 3009.Separating force should be understood to and acts on the tip of the tongue 3010 or act on the separator levers and be delivered to maximum, force on the dish spring 3009 when friction clutch 3001 operation.In order to realize the consummating function of friction clutch, by the member 3009 of dish spring form and when needed by other parts, axially making a concerted effort as leaf spring 3015 generations, it acts on the dish spring 3004 and greater than maximum separation power, yet less than the remaining force that acts on platen 3003 by dish spring 3004.The power of supporting dish spring 3009 must be resisted possible perturbed force on the other hand, as the inertial force that is occurred by axial vibration.The parts 3009 of this dish spring form can constitute like this with advantageous manner, and promptly its value of acting on the axial force on the operation dish spring 3004 is 1.1 to 1.4 times of maximum separation power.

Shell-side ring-shaped bearing or pivoting support 3005 are combined in the regulating device 3017.This regulating device 3017 at first plays the effect that makes 3004 axial displacements of dish spring corresponding to the wearing and tearing of the rubbing surface of friction lining 3007 and/or platen 3003 or flying wheel 3006, and and then guarantee: when dish spring 3004 on the direction of platen 3003 or in axial displacement on the direction of back-pressure plate 3006 time, at pivoting support 3005 and shell 3002 or between pivoting support 3005 and dish spring 3004, can not form undesirable gap.Just guaranteed thus when friction clutch 3001 operation, not form undesirable any invalid or idle stroke, and therefore obtained optimum efficiency and obtained the perfect operation of friction clutch 3001 thus.The self-adjusting action principle of this pivoting support 3005 will be in conjunction with Figure 62 A, 66A, and 62B to 66B further specifies.

What regulating device 3017 comprised an annular construction member form applies the adjustment component 3018 of spring force at circumferencial direction, and it has constituted a wear compensation ring.This wear compensation ring 3018 has on circumference the rising sloping platform 3019 that extends and rise in the axial direction, and it is distributed on the circumference of parts 3018 and is similar to another annular element 3020 shown in Figure 61, and the latter is the member of regulating device 3017 equally.This wear compensation ring 3018 is contained in the clutch 3001 in this wise, and sloping platform 3019 3002a at the bottom of the shell promptly rises.Carrying at this wear compensation ring 3018 on the side of rising sloping platform 3019 is the pivoting support 3005 that the metal loop of centralized positioning in a groove shaped seat constitutes.This pivoting support 3005 also can constitute one with wear compensation ring 3018.

Rising sloping platform 3019 axially is bearing on the opposed rising sloping platform 3021, and the latter directly is contained in shell 3002 and promptly covers among the end 3002a in illustrated embodiment, and to Figure 61 in similar about the situation shown in the opposed rising sloping platform 3022 of ring-shaped member 3020.This annular element 3020 has rising sloping platform 3023, and the rising sloping platform 3019 of it and wear compensation ring 3018 similarly is made of wedge shape and claw-form 3024.

Opposed rising sloping platform 3021,3022 are made of the axial die castings that is contained in the lid, wherein from circumferencial direction, between the zone that constitutes these opposed rising sloping platforms, can have axial gap or interrupt 3025, as among Figure 61 about shown in the lid zone 3026 that constitutes opposed rising sloping platform 3022.Die castings 3026 is to constitute like this: on the sense of rotation of friction clutch 3001, die castings 3026 region in front are regional or axially stretch out with respect to the rear region of adjacent die castings 3026 with respect to adjacent cover, and these die castingss or profiled member 3026 play the effect of flabellum thus.When rotating, friction clutch 3001 plays the effect that enters the air circulation in the space in the clutch that forces by these holes or breach 3025, the heat load of friction clutch and the especially heat load of friction lining 3007 are descended significantly, and make the corresponding prolongation of its life-span.This annular construction member 3018,3020 can be by plastics, and for example a kind of heat-resisting plastics make.These parts 3018,3020 can be made as plastic-blasting spare of simple mode thus.Yet these parts also can be made of sheet component or sintered component.Utilize the favourable configuration of vent hole 3025 that the heat load on the annular element 3018,3020 is obviously reduced, this point is particular importance when adopting plastics especially.

Rising sloping platform 3019 and 3023 and their set opposed rising sloping platforms 3021 and 3022 are constituted in this wise in a circumferential direction: shell 3002 make wear compensation ring 3018 and the sensing ring 3020 that weares and teares rotates an angle at least relatively, and thus can the whole duration of work of friction clutch at least to platen 3003, opposed platen 3006 and friction lining 3007 on the compensation of occurring wear promise.Must consider that to this when reaching total wear extent of maximum permission, what the contact surface that also has will be enough is big, so that resistant function axial force thereon between each sloping platform 3019,3021 and 3022,3023.This point counts for much to wear compensation ring 3018 especially, and it is supporting whole pressure of dish spring 3004.The value at this torsion angle or adjustment angle is looked the configuration of rising sloping platform 3019,3023 and opposed rising sloping platform 3021,3022 and is decided, and between 10 and 90 degree, is preferably the magnitudes of 30 to 80 degree.These rising sloping platforms 3019,3023 and opposed rising sloping platform 3021,3022 the magnitudes that angle or the angle of climb 3027 are 4 to 30 degree when favourable mode axially are set, preferably its magnitude is 4 to 15 degree.In this illustrated example, this angle 3027 is about 12 degree.What meet the requirements especially is that this angle 3027 is selected in this wise, promptly at rising sloping platform 3019,3023 and the friction energy that forms when pressing mutually each other of opposed rising sloping platform 3021,3022 prevent from slip between the sloping platform staggered relatively from just in fact to have formed one from resistance by friction.When determining this angle 3027, also must consider by adjusting spring 3028 and 3029 acting on wear compensation ring 3018 on the round direction and/or wasting the power of decreasing on the sensing ring 3020.The rising sloping platform that wear compensation ring and wearing and tearing sensing ring are provided with and the angle of elevation 3027 of opposed rising sloping platform can be identical.These two rings also can be provided with the sloping platform of different sizes and different angle of elevation 3027.

Wear compensation ring 3018 is applied in spring force in a circumferential direction, and on the adjustment sense of rotation, work, just working on such direction: the slip by sloping platform 3019 and opposed sloping platform 3021 makes wear compensation ring 3018 produce an axial displacement on the direction of platen 3003, this means leaving on the axial direction of shell section 3002a radially.Wearing and tearing sensing ring 3020 also is spring loaded on the adjustment sense of rotation with similar mode.In the embodiment shown in Figure 59 and 60, the spring-loaded of wear compensation ring 3018 is guaranteed by at least one helical spring 3028.In illustrated embodiment, be tandem arrangement using when these two rings 3018 and 3020 have connected spring 3029 in the centre, so that by the adjustings of spring 3028 same realization wear sensors 3020.Helical spring 3028 is received within on one sheet 3030, and this sheet and clutch cover 3002 constitute one.This sheet 3030 is for example to be rushed out a U-shaped breach 3002c and moulding by lid 3002 sheet material.From circumferencial direction, these sheet 3030 arcs or the tangential regional identical axial height of lid that extends and preferably have approaching at least and direct neighbor.The width of this sheet 3030 is to set like this, and it not only radially but also axial is all leading to helical spring set on it 3028.

The wear compensation ring 3018 that is loaded on the adjustment direction by spring 3028 has radially inner carriage 3031 on the circumference within it at least, and it stretches between lid 3002 and dish spring 3004.Fork or U type member 3032 that carriage 3031 has an axial orientation in inner radial, its two axial tenons 3023 prop up sheet 3030 round the spring guiding on both sides.These two tenons 3033 axially stretch into or pass the breach 3002c that covers on 3002 for this reason.Adjustment spring 3028 at U type spare 3032 or tenon 3033 upper supports, and thus in a circumferential direction to wear compensation ring 3018 application of forces, the platform 3019 of it and corresponding inclination and opposed sloping platform 3021 formed one leave cover 3002 and on the direction of dish spring 3004 to encircling 3018 and axially directed to support 3005 thus axial members.

Wear compensation ring 3018 has a radially carriage 3034 at least at radial outside, sees it and radially a carriage 3035 being provided with of inner region is overlapping diametrically at wearing and tearing sensing ring 3020 from circumferencial direction.In carriage 3034,3035, be provided with breach or hole 3036, in these holes, placing the helical spring 3029 that between two rings 3018 and 3020, imposes very little precompression at least.Utilize carriage 3034 backstops on carriage 3035, can limit wear compensation ring 3018 relatively moving with respect to wear sensor 3020.

Friction clutch 3001 also has a wear sensor 3037, and in the embodiment shown in Figure 59, it is that parts 3037 by dish spring shape or film shape constitute.These film shape parts 3037 its cyclic spring zones 3038 extend on dish spring 3004 sides of platen 3003 and the most handy certain axial projection part towards the direction upper support of wearing and tearing sensing ring 3020 on the latter.This film member 3038 and dish spring 3004 diameters are fixedly connected and be connected by riveting parts 3039 to inside, also can use other Placement, as between dish spring 3004 and film member 3037 the clamping-type interlocking being set.This cyclic spring zone 3038 is provided with breach 3040 on the radial height of the tongue 3009a of supporting dish spring 3009, by it the support region of tongue 3009a is axially passed.Guaranteed that thus tongue 3009a does not exert an influence to the resiliently deformable of film 3037.These film shape parts 3037 radially outers have axial region 3041, and it has constituted the axially mounting zone to wearing and tearing sensing ring 3020.

Make film member 3037 be pressed in ring 3020 and be pressed in precompression on dish spring 3004 outer rims be chosen such that in clutch and produce wearing and tearing or situation that wearing and tearing have compensated under wearing and tearing sensing ring can not rotate.Also must consider when friction clutch is worked, to pass through each parts at design this spring or film member 3037 and act on perturbed force on these parts 3037, as inertial force.Must guarantee by the precompression by parts 3037, by axial vibration, the axial force that for example causes parts 3037 shifting grounds are resisted, and this especially must be guaranteed under the state that friction clutch engages because of parts 3020.

Must avoid a kind of is not by wearing and tearing, especially the rise of the wear sensor 3037 that causes of liner wearing and tearing from the wearing and tearing sensing ring 3020, because otherwise just have danger, the sensing of promptly wearing and tearing ring 3020 carries out once undesirable rotation or adjustment, and wear sensor 3037 keeps pressurized thus, may produce the out of control of friction clutch adjustment like this.Now the working principle of regulating device 3017 will be described further in conjunction with Figure 62 A to 66A and 62B to 66B.

At the component locations shown in Figure 62 A and the 62B is the position that is had under the new state of the friction lining 3007 of friction clutch 3001 or clutch disk 3008, and this friction clutch 3001 is in jointing state.Be equivalent to normal given air gap in the outer rim of dish spring 3004 and towards its supporting or the distance L between the stop surface 3020a of wearing and tearing sensing ring 3020 in this state, it has determined the given upward stroke of platen 3003.The film shape parts 3037 that constitute wear sensor in this new state are axially put in the outer diameter zone of dish spring 3004, and are stoping the rotation of wear sensor ring 3020.This wearing and tearing sensing ring 3018 is to keep rotation inhibiting by the supporting force of transmitting by dish spring 3004.

As appreciable from Figure 62 B, the pawl 3034,3035 that constitutes limit stops contacts each other.Make also that thus ring 3018 prevents to rotate.The spring 3029 that is provided with between two rings 3018,3020 is compacted by the power that applies by adjustment spring 3028.The adjustment power that is applied by spring 3028 during whole operating life is also promptly being encircled 3018,3020 whole rotation or is being adjusted the adjustment power that this spring 3028 applies on the stroke, must be greater than spring 3029 applied force in its compacted position of Figure 62 B.

When friction clutch 3001 separated, the dish spring changeed supporting 3005 revolutions and inclination from the wraparound of position shown in Figure 62 A, as appreciable by Figure 63 A, touched with its outer rim on the stop surface 3020a of wearing and tearing sensing ring 3020 after separating stroke X through one.The stroke L1 that made platen 3003 axial displacements thus promptly removes from the O-position.In this separation phase of friction clutch 3001, this elastic member 3037 is at axial pressurized additionally.Guaranteed thus: when friction clutch separates, at first make wearing and tearing sensing ring 3020 on the direction of lid 3002, be subjected to a power that increases, therefore avoided the adjustment of undesirable ring 3020 through revolution stroke with the corresponding dish spring of distance L outer rim.As seeing from Figure 63 B, the angular orientation of these two rings 3018 and 3020 does not change.

Stroke X is corresponding to the minimum separation stroke that reaches platen 3003 upward stroke L1 and guarantee the required minimum stroke of adjustment function.

In order to realize this minimum stroke, in the piece-rate system of an automobile, be provided with separation stroke usually greater than X, it counts increase stroke Δ X here owing to the reason of tolerance and vibration may be bigger.When surpassing minimum separation stroke X, dish spring 3004 is lifted super from pivoting support 3005, make thus between dish spring 3004 and the pivoting support 3005 gap 3042 to have occurred.Yet can't realize the adjustment of wear compensation ring 3018, this is because as seeing from Figure 64 B, two backstop pawls 3034,3035 contact with each other, and wearing and tearing sensing ring 3020 also additionally prevents to rotate by dish spring 3004 or by the compressing of support spring 3009 that dish spring 3004 is pressed on the ring 3020.As from Figure 62 A, appreciable among 63A and the 64A, variation has also taken place in the inclination of support spring 3009 when friction clutch 3001 separates.

If in friction clutch operation or when friction clutch engages, produced wearing and tearing, for example be the wearing and tearing on the friction lining 3007, then platen 3003 will move one corresponding to the value 3043 (Figure 65 A) of wearing and tearing in axial direction towards opposed pressing plate 3006.Because this axial displacement makes the inclination of dish spring 3004 and support spring 3009 or the angle is set and changes, and dish spring 3004 on its tip of the tongue zone 3010 with respect to position axis shown in Figure 62 A to displacement to the right an amount Δ Y.Because the variation of dish spring 3004 inclinations, the support region 3041 of this wear sensor 3037 are also axially left wearing and tearing sensing ring 3020 to left dislocation, and its displacement is value 44.Just make wearing and tearing sensing ring 3020 releases or make for the rotation under spring 3029 effect and to discharge and thus through the axial displacement of sloping platform 3022,3023.Till when the power that the rotation of wearing and tearing sensing ring 3020 is performed until spring 3029 no longer is enough to make the ring 3020 that rotates on support region 3041 to be rotated further.Yet the rotation of wear compensation ring 3018 is impossible, because at this moment it is by dish spring 3004 axial force distributions.Rotation by wear compensation ring 3020 has formed a gap or distance 3045 between these two backstop pawls 3034,3035, as appreciable from Figure 65 B.This distance 3045 is approximately corresponding to the axial displacement 3044 of wearing and tearing sensing ring 3020 tangent divided by the angle 3027 of rising sloping platform 3023 or opposed rising sloping platform 3022.

Because making, attrition value 3043 engages stroke Y with respect to separate stroke X+ Δ X big value Δ Y.

During the separation process of the friction clutch after following the above-mentioned engaging process that has wearing and tearing, will be with to combine Figure 64 A similarly described, 3018 releases of wear compensation ring, but now wherein owing to exist as the distance 3045 between two backstop pawls 3034 among Figure 65 B and 3035 wear compensation ring 3018 is adjusted.This adjustment is because the precompression of spring 3028 causes, this precompression is greater than making the required power of spring 3029 compressions.Adjustment by wear compensation ring 3018 contacts pawl 3034 and 3035 again, as from Figure 66 A, seeing, so that when friction clutch is rejoined or is closed, though dish spring 3004 has moved the distance value corresponding to wear extent in the axial direction, obtained in fact again with Figure 62 A in identical angular orientation.Yet can see that from Figure 66 B these two are encircled the 3018 and 3020 original angle positions with respect to Figure 62 B and on the adjustment direction rotation taken place.

Also can find out from Figure 66 A, adjust the parts 3009 of dish spring shape and also changed its inclination owing to realized wearing and tearing.

In conjunction with Figure 62 A to 66A and the described adjusting of 62B to 66B is to carry out with very little paces in practice, lasting adjustment also promptly takes place during its operating life, so that in practice because the adjustment amount that wearing and tearing take place is very little, in these figure, corresponding distance and adjustment amount are described to such an extent that more only be in order to understand better.

As described in conjunction with Figure 63 A and 64A, radially outer at dish spring 3004 behind the predetermined separation stroke X is bearing on the wearing and tearing sensing ring 3020, so that the turning spur of dish spring 3004 moves on the zone of surface of contact 3020a from pivoting support 3005 radially outwards.Be dish spring 3004 originally as double-arm lever, on the height of pivoting support 3005, rotate around supporting; When surpassing this and separate stroke X, then this dish spring such as same single-arm lever are supported, and are supported pivotally or are keeping because be actually its radially outer edge zone.Dish spring lever ratio is similar to from i changes to i+1, wherein i is that radial distance between the loading diameter of Separating force in pivoting support 3005 and the tip of the tongue 3010 zones is to the ratio of radial distance between the loading diameter of 3003 of pivoting support 3005 and dish spring 3004 and platens.This is external to need when considering dish spring 3004 regarded as at least with the supporting between the sensing ring 3020 of wearing and tearing and is similar to, and being bearing on the same radial height between dish spring 3004 and the platen 3003.Power-stroke curve that change or increase by dish spring lever ratio makes this cup spring flattens smooth, this means, in case this lever ratio is strengthened, the variation of power or power then can reduce on stroke, and just the dish spring has more smooth or softer power-stroke curve in the zone of big power transmission ratio.Can realize the decline of Separating force curve in this zone thus.

Similarly constitute a kind of so-called pressure type friction clutch at the friction clutch 3101 shown in Figure 67 A.Dish spring 3104 is bearing in two pivoting supports 3105 with shell 3102 axial restraints pivotally, between the 3105a.Axial restraint for these two pivoting supports 3105 and 3105a and its middle set dish spring 3104 is provided with holding device 3102b, and it is connected with lid 3102.In this illustrated embodiment, this holding device 3102b is by constituting from covering the sheet 3102b that a figure modelling goes out, it passes the extension of dish spring 3104 ground in the axial direction, and backstop stays in the pivoting support 3015a that is provided with on dish spring 3104 sides of platen 3103 in the axial direction.

This friction clutch 3101 also has a wear sensor 3137, and this sensor has the zone 3138 of a ring-type elastically deformable, and it is used as riveted fixing on lid end 3102a.This wear sensor 3137 have extend axially the zone 3141, it axially passes dish spring 3104.This zone 3141 constitutes the support region 3141a for wearing and tearing sensing ring 3120.

Between a wearing and tearing sensing ring 3120 and the sheet 3102b lower zone axially on have an axial clearance L, the axial displacement of platen 3103 when it has determined that friction clutch 3101 separates.

The radially outer of dish spring 3104 is bearing on the metal loop 3118a, and the latter adjusts ring 3118 by wearing and tearing and supporting.

Wear compensation ring 3118 and wearing and tearing sensing ring 3120 axially axially are bearing on the platen 3103 by sloping platform 3119,3123 and opposed sloping platform 3121,3122.These sloping platforms 3119,3123 and opposed sloping platform 3121,3122 with regard to the shape of its circumferencial direction and angle of elevation its structure with to combine the described person of Figure 59 to 66 similar.In form of implementation, be preferably on the regulating device 3117 and need have self braking on the direction facing to adjusting according to Figure 67.

Opposed rising sloping platform 3121,3122 directly moulding on platen 3103, but but also be provided with at least axially be formed in a ring 3118 or 3120 and platen 3103 between the parts of an opposed rising sloping platform, but its same looping.Best and anti-being rotationally connected of platen 3103 formation of these parts.Also can be that ring 3118 and/or 3120 forms anti-the rotation but axially displaceable the connection with platen 3103, and constitute the parts of opposed rising sloping platform can be with respect to platen 3103 rotations.

Abrasion detection ring 3120 and wear sensor 3137 actings in conjunction, the latter is made of axial telescopic parts at least.This wear sensor 3137 can be distributed on the circumference by one or more, axially the hook of elastically deformable constitutes, or constitute by the parts with cyclic spring matrix 3138, radially inwardly extending each sheet 3141 by this matrix, this sheet contact is on abrasion detection ring 3120.But the wear sensor 3137 that is somebody's turn to do elastic telescopic must have a basic deformation force or basic precompression, and it guarantees that all the time abrasion detection ring 3120 can not adjusted when not occurring wearing and tearing.Also must make corresponding alignment to each spring that acts on wearing and tearing adjustment ring 3118 and/or 3120 effects of abrasion detection ring.

Platen 3103 is faced toward shell 3102 pressurizeds in this wise via spring element, promptly need to guarantee all the time, under the situation that clutch 3101 separates platen 3103 is held all the time is pressed on the dish spring 3104, also is that pivoting support 3118 keeps in touch with dish spring 3104 all the time.This hold down gag for example can pass through elastic device, constitutes its available corresponding precompression assembling, similar to shown in Figure 59 as plate spring component.When design dish spring 3104, should consider to react on the power applied force of dish spring 3104 by this device.Should consider during the axial pressing device of this external design platen 3103 and shell 3102 because power that produces at inertia, the especially inertia of platen 3103 of the parts of axial motion and the power that causes by the acceleration that the vibration of these parts produces.

The upward stroke of platen 3103 is provided with a stop member when separating in order to be limited in friction clutch 3101, is by support region 3141a the contact of the lower area of a sheet 3137 to be realized in illustrated embodiment.The ventilation stroke of platen 3103 is determined by gap L.

The corrective action of regulating device 3117 can be compared with the regulating device 3017 according to Figure 59 to 66.Figure 67 is illustrated in the new state that is assembled to the friction clutch 3101 in the state on the opposed pressing plate.As long as wearing and tearing occurred on the friction lining that does not illustrate again, platen 3103 is moved to the left corresponding to wearing and tearing, so that abrasion detection ring 3120 can be made adjustment corresponding to wearing and tearing.Between the backstop pawl of these two rings 3118,3120, circumferential clearance occurred thus, be similar in Figure 65 B represented with pawl 3034,3035.When friction clutch 3101 separated, at first platen 3103 and two rings 3118,3120 moved axially towards lid end 3102a direction jointly, and wherein sensor 3137 flexibly is out of shape.After having overcome gap L, platen 3103 reaches at the abrasion detection ring 3120 that axially pressurizes, is pressed on the platen by wear sensor 3137 and stops.The separation stroke of friction clutch 3102 limits in this wise: at least after overcoming gap L under the situation that has wearing and tearing, dish spring 3104 also will change a definite angle and just arrive on its inclination, making wearing and tearing adjust axially unloading and adjust of ring 3118 thus, and measuring accordingly with the transmission of abrasion detection ring 3120 the preceding and to adjust by rotating one with respect to the liner wearing and tearing that exist.After this rotated, the backstop of these two rings 3118 and 3120 contacted again, was similar in Figure 70 for shown in the thrust pawl 3334,3335.Because this backstop is spacing, dish spring 3104 can make ring 3118 unloading fully, because this ring can not adjusted out of control by backstop.

Constitute a so-called pressure type clutch at the friction clutch shown in Figure 68 3201, its operation dish spring 3204 is crushed on or pulls on the pivoting support 3205 that covers side.Be provided with the power storage 3209 of a dish spring form for this reason, it be crushed on clutch housing or cover 3202 and platen 3203 between.This dish spring 3209 is set on the side of carrying the lid 3202 of operating dish spring 3204 and by connection set 3209a and is connected with platen 3203.This connection set 3209a passes and is located at the hole in the dish spring 3204 and extends.Yet this dish spring 3209 also can directly be located at cover 3202 and platen 3203 between.The axial force that is applied by this power storage 3209 is to limit like this: this power is greater than being used for the required maximum separation power of cut-off clutch 3201, and this maximum separation power is that to make the dish spring 3204 that is contained in the clutch 3201 produce revolution required.What meet the requirements is, the elastic pressure that acts on platen 3203 by power storage 3209 during the operating life of friction clutch 3201 is at least 1.1 * maximum separation power.Yet the axial force that is applied by this power storage 3209 in fact can be bigger.The person of meeting the requirements also is, this dish spring 3209 has in fact constant stroke-force curve during the operating life of friction clutch 3201 or during the maximum possible compensation stroke of experience controlling device 3217, so that in fact the impacting force that acts on platen 3203 by dish spring 3204 keeps constant.Yet so also be favourable: dish spring 3209 has predetermined power-stroke characteristic on the adjustment range of regulating device 3217, the impacting force of the leaf spring that the increase of wearing and tearing with liner in order to compensation increases, this leaf spring is transmitting torque between shell 3202 and platen 3203.This leaf spring is represented with label 3015 in Figure 59.

Axially set wear compensation device 3217 has a wear compensation ring 3218 and an abrasion detection ring 3220 between dish spring 3204 and platen 3203, and they are similar at two rings 3118 and 3120 arranging and act on to according to Figure 67.These two rings 3218,3220 are bearing on the opposed rising sloping platform 3221,3222 of platen 3203 by rising sloping platform 3219,3223.Wear sensor 3237 is to be made of membranaceous or dish spring shape parts, and it is fixed on the dish spring 3024 by the connection of riveting 3239 forms in inner radial.This of wear sensor 3237 for example has a distance L facing to dish spring 3204 in annular spring zone 3238, and it has determined the upward stroke of platen 3203 when friction clutch 3201 separates.These wear sensor 3237 its radial outer ends by the elasticity precompressed are bearing on the face of carrying ring 3218,3220 of dish spring 3204.Elastic region 3238 has axially extended sheet 3241 at radially outer for this reason, and this sheet passes the axial holes of dish spring 3204 and led dish spring 3204 and carry on the face of this elastic region 3238 and be bearing on this face.This elasticity wear sensor 3237 thereby flexibly be pressed on the operation dish spring 3204.Can avoid the adjustment of undesirable abrasion detection ring 3220 by elasticity sensor 3237.These two rings 3218 and 3220 are memory load firmly in a circumferential direction, is similar in conjunction with the figure of front described.

From the separation of the engagement positio shown in Figure 68 friction clutch 3201 time, dish spring 3204 makes platen 3203 unload, and passes through power storage 3209 at the detaching direction top offset around ring-shaped bearing 3205 revolutions.Abrasion detection ring 3220 is towards the 3204 direction displacements of dish spring in separation process, so that wear sensor 3237 resiliently deformables, and till being performed until cyclic spring zone 3228 and 3204 formation of dish spring contacting, in fact the axial displacement of platen 3203 on detaching direction finished, make 3218 unloadings of wear compensation ring when on detaching direction, continuing distortion with convenient dish spring 3204, only otherwise have the liner wearing and tearing, wear compensation ring 3218 is just static with respect to platen 3203, because the stop member of two rings 3218 and 3220 contacts, be similar in Figure 62 B to 64B for shown in the backstop pawl 3043,3035.Abrasion detection ring 3220 itself is being pressed platen 3203 by wear sensor 3237, so that this ring can not rotate yet.

In case for example wearing and tearing occurred on the friction lining, platen 3203 is moved to the left, and makes the also slight change of inclination of dish spring 3204 thus.Because this displacement just makes 3220 unloadings of abrasion detection ring, and this ring is adjusted corresponding to wearing and tearing, this adjustment at this moment will be worn the restriction of sensor 3237.If now this friction clutch 3201 separates again, then with combine the described similar ground of Figure 67,3218 unloadings of wear compensation ring, this ring can be adjusted thus, and is performed until between two rings 3218 and 3220 till the formation backstop action.

Each adjusting stage that reaching between the ring 3118 and 3120 among Figure 67 encircled among Figure 68 between 3218 and 3220 is corresponding to each stage shown in Figure 62 B to 66B.

Constitute a kind of what is called at the friction clutch shown in Figure 69 to 71 3301 and be subjected to pull-type friction clutch.The radially outer of dish spring 3304 is bearing on the wear compensation ring 3318 set between the radial zone 3302a of shell 3302 and the dish spring 3304.Its radially interior zone of dish spring 3304 usefulness is to projection 3303 application of forces of a platen 3303.Carry at dish spring 3304 on the face of platen 3303 and be provided with a wear sensor 3337, it by 3304 supportings of dish spring and with the latter by the snap fit latch.The wear sensor 3337 that for this reason constitutes the dish spring has at radially outer and constitutes hook-shaped axial arm 3341, and this arm combines with axial bore 3304a set in the dish spring and constituted a grafting of axially interlocking-be rotationally connected.Has a sheet 3341a who in the tip of the tongue zone, extends in order to make these two parts 3304 and 3337 be fixed on dish spring 3337 inner radial on this position of playing the interlocking effect, this dish spring 3337 axially is being pressed on the dish spring 3304 and after having made the rotation of interlocking effect between these two parts 3337 and 3304, this sheet 3341a snaps fit onto among the hole 3304b of dish spring 3304 in order to preventing and rotates.This wear sensor 3337 is avoided the adjustment of abrasion detection ring 3320 under the situation of not depositing wearing and tearing.This abrasion detection ring 3320 is arranged on the inner radial of wear compensation ring 3318 with one heart.

With the description of the figure that combines the front especially Figure 59 and 60 similarly, these two rings 3318 and 3320 axially are bearing on the opposed rising sloping platform 3321,3322 that is supported by shell 3302 through rising sloping platforms 3319,3323.

As seeing from Figure 70, two rings 3318,3320 similarly have backstop pawl 3334,3335 with ring 3018,3020, are being pressed a helical spring 3329 between these two backstop pawls.

As appreciable from Figure 70, wear compensation ring 3318 is being adjusted the application of force on the direction by the power storage 3328 of a helical spring form.Power storage 3328 is set in these two radial zones between ring 3318 and 3320 the annular matrix.With the description that combines Figure 59 and 60 similarly, this spring 3328 is received within and covers on 3302 the tongue spare or a sheet 3330.Wearing and tearing adjust ring 3318 also with Figure 59 and 60 in ring 3018 have a carriage 3331 similarly, it has a forked type spare 3332 that is used for support spring 3328.This spring 3328 here, wear compensation ring 3318, spring 3329, wear sensor 3320 and wear sensor 3337 are used also at it and are connected in series.

Wear sensor 3337 has avoided occurring the adjustment of unallowed wearing and tearing sensing ring 3320 when not having wearing and tearing, itself has avoided the adjustment of unallowed wear compensation ring 3318 again the sensing ring.

From shown in Figure 69 in the new state that is installed in a friction clutch 3301 on the opposed pressing plate under the situation that accompanies clutch disk 3316, when friction clutch 3301 separates, the radial inner end of dish spring 3304 turns right, so that the radially outer of dish spring 3304 is bearing on the pivoting support 3305 that is supported by wear compensation ring 3318.In this separation phase, sensing dish spring 3337 axially is crushed between cup spring 3304 and the wearing and tearing sensing ring 3320, and until between the perimeter of cyclic spring sections of sensors 3338 and dish spring 3304 really the gap L of level pressure dish 3303 rising values be eliminated, also be till dish spring 3304 itself axially is bearing on the sensing ring 3320 that weares and teares.Dish spring 3304 will be around the ring-shaped bearing zone 3320a revolution on the wearing and tearing sensing ring 3320 when continuing detaching motion, the pivoting support 3305 that makes radially outer thus is from 3304 releases of dish spring, so that when having wearing and tearing, can compensate this wearing and tearing to adjustment by encircling 3318 corresponding axis.Originally this dish spring 3304 is similar to single-arm lever around outside pivoting support 3305 revolutions at separation phase.After having overcome gap L, the annular turning circle of dish spring 3304 radially is moved on the regional 3320a of wearing and tearing sensing ring 3320, thereby 3304 of dish springs are similar to the double-arm lever revolution or work when detaching motion continues.Radial displacement by this dish spring 3304 annular pivoting supports, power transmission ratio or lever ratio when friction clutch 3301 operations, have just been changed, this lever ratio has determined the power that operation dish spring 3304 is required, it changes to i-1 from i, in case when therefore dish spring 3304 is bearing on the wearing and tearing sensing ring 3320, the raising of Separating force can occur.Power transmission is the ratio of the zone of action to the distance of the contact area of 3305 of dish spring 3304 and pivoting supports and this contact area to the distance between the application of force zone of the projection 3313 of 3304 pairs of platens 3303 of dish spring of Separating force in dish languid point 3310 territories than i.The variation of above-mentioned power transmission ratio is based on such hypothesis, i.e. supporting between dish spring 3304 and the platen 3303 occurs on the diameter identical with the supporting of 3304 pairs of wearing and tearing of dish spring sensing ring 3320 at least approx.The support region that dish spring 3304 and wearing and tearing sensing ring are 3320 moves more greatly towards the direction radially outward of pivoting support 3305, and the rising of Separating force was just little when then dish spring 3304 contacted with wear ring 3320.

In case wearing and tearing occurred on the friction lining 3307 when zygophase, dish spring 3304 will change its inclination and its tip of the tongue 3310 is shifted to left.Variation by this inclination makes 3320 unloadings of wearing and tearing sensing ring, and this ring can be adjusted corresponding to the liner wearing and tearing that occur.At first be that wearing and tearing sensing ring 3320 adjusts prior to wear compensation ring 3318 when wearing and tearing occurring, as shown in Figure 70.Rotation by wearing and tearing sensing ring 3320 distance that is directly proportional with wear extent 3345 occurred between the thrust pawl 3334 and 3335 of two rings 3318,3320.In the separation process of following from now on, as the figure by the front described, wearing and tearing are adjusted ring 3318 by 3304 unloadings of dish spring, so that this ring is adjusted with respect to gap 3345.Make dish spring 3304 obtain inclination or the plan-position suitable again thus with new state.Along with the increase of wear extent, dish spring 330 will cover end 3302a axially removing, and proofread and correct so realized the respective angles of dish spring mounting point on whole adjustment region.This is corresponding always proofreaies and correct according to being caused by 3320 wearing and tearing that obtain or that measure of wearing and tearing sensing ring.

Regulating device 3417 its structures of the part shown in Figure 72 with arrange to similar by the wear adjustment device 3317 of Figure 69 and 70.It and be according to the substantive difference of the form of implementation of Figure 69: abrasion detection ring 3420 is arranged in the radial zone between the supporting point of the supporting point of projection 3413 of 3404 pairs of platens 3404 of dish spring and the pivoting support 3405 that 3404 pairs of dish springs are located at radially outer.The sensing ring 3420 that also promptly weares and teares has bigger diameter, and is nearer so that the supporting that produces between cup spring 3404 and wearing and tearing sensing ring 3420 when the friction clutch separation phase is adjusted ring 3418 from wearing and tearing.Making the increase of the Separating force that takes place when dish spring 3404 touches wear ring 3420 thus is to have reduced with respect to the form of implementation according to Figure 69.This sensing dish spring 3438 is similar to dish spring 3338, is affixed on the dish spring 3404 with joint and clinging type.

In the form of implementation according to Figure 72, the spring travel S that can be returned on the radial height of the supporting diameter between wearing and tearing sensing ring 3420 and the dish spring 3404 by sensor 3438 is setting like this: rising of returning from platen when friction clutch separates or ventilation stroke multiply by ratio L2/L1 at least approx corresponding to the spring travel s of sensor 3438.Therefore at sensor 3438 relation below the existence: V=S * (L1/L2) at least approx between the whole rising of spring travel possible on the radial height of the supporting diameter of 3404 of wearing and tearing sensing ring 3420 and cup springs and platen 3403 or ventilation stroke " V ".

Have a controlling device 3517 at the draw-off type friction clutch 3501 shown in Figure 73, it axially is arranged between dish spring 3504 and the platen 3503.The radially outer of this dish spring 3504 is bearing on the pivoting support 3505 that is supported by clutch cover 3502, and with its radially interior area supporting on wear compensation ring 3518, the latter axially is bearing on the platen 3503.This wear compensation ring 3518 sensing ring 3520 that is worn surrounds.These rings 3518,3520 also have rising sloping platform 3519,3523, and they axially are bearing on the opposed rising sloping platform 3521,3522 that is supported by platen 3503.Between dish spring 3504 and the wearing and tearing sensing ring 3520 axially on a wear sensor 3537 is also arranged, it is made of a film member.This elastic member 3537 is supported by dish spring 3504, and is to set like this and install, and promptly these parts 3537 compacted needed power are greater than adjustment power, and this adjustment power is to act on the sensing ring 3520 that weares and teares in the axial direction.Adjust ring 3518 and can not rise in order to guarantee when having axial vibration platen 3503 or wearing and tearing from dish spring 3504, platen 3503 is axially being pressed facing to shell 3502 by the spring members of dish spring 3509 forms, and is to the pivoting support 3505 towards the lid side.Guaranteed also that thus wearing and tearing sensing ring 3520 can not rise from wear sensor 3537.

In case the wearing and tearing of friction lining occurred, the angular orientation of dish spring 3504 or gradient just produce and change and be such: the radially inner region of dish spring 3504 is turned round left and corresponding to the axial displacement of platen 3503.Make 3520 unloadings of wearing and tearing sensing ring thus, make adjustment to cause this wearing and tearing sensing ring relative wear, and this adjustment is by wear sensor 3537 restrictions.In a single day reach the predetermined upward stroke of platen 3503 in a back to back separation phase, then wearing and tearing are adjusted ring 3518 by 3504 unloadings of dish spring, make this wear adjustment ring 3518 move the stroke of adjusting in advance corresponding to by the sensing ring 3520 that weares and teares thus.

The available stop member to dish spring 3504 perimeters of the restriction of platen 3503 axial separation strokes is realized.Yet travel limits also can realize with stop member in other position, for example can directly establish a corresponding stop member between shell 3502 and platen 3503.Be used for the required power of jam sensor 3537 in fact less than the active force that acts on by dish spring 3509 on the platen 3503.So wear sensor 3537 compresses via dish spring 3509 when friction clutch 3501 separates.

For the major applications situation, the radial distance that the revolution of the sensing of advantageously wearing and tearing ring or support region and wearing and tearing are adjusted between loopback commentaries on classics or the support region approximates operation dish spring to the supporting point of lid and the radial distance between the point of application of force between operation dish spring and platen.Can guarantee thus: when wear adjustment, the axial stroke of being returned by wearing and tearing sensing ring equals the axially wear extent of generation at least approx.

In Figure 74 and a kind of wear sensor of 75 expressions unit, it constitutes a spring clip 3637.A plurality of such sensor units 3637 can be located on the circumference of the elastic ring body of operating dish spring 3604 equably.As finding out from Figure 74, such spring clip 3637 is connected with dish spring 3604 by clamping, or the end regions of two outer leg 3637a by penetrating spring clip and middle leg 3637b driven on the outer rim that is connected on dish spring 3604 is connected with the dish spring.For example can be used in the form of implementation according to a kind of friction clutch of Figure 59 according to the wear sensor unit of Figure 74 and 75.

As describing in conjunction with Figure 59, advantageously friction clutch has a kind of device, it plays the effect that the moment by the friction clutch transmission is reduced gradually when separation phase, because can reach the decline of Separating force curve or required maximum separation power thus or reduce to minimum.At this device on the friction clutch shown in Figure 59 is to be made of the packing spring section 3016 that is provided with between friction lining 3007.This packing spring section is for example known by DE-OS3631863.

Another kind of at friction clutch separation or realize that moment descends gradually or the possibility that raises is provided by DE-OS2164297 when engaging.Flying wheel is made of two-part in this technical solution, and the component axial that constitutes opposed pressing plate flexibly is bearing on the parts that are connected with the internal combustion engine drive axle.

A kind of device of replacing packing spring also can be arranged in the power system between extrusion spring 3004 and the platen 3003.This device is proposed by DE-OS3742354 and DE-OS1450201.The device that substitutes packing spring can be located in addition in the power system between extrusion spring 3004 and the fixed position, this fixed position for example is that shell 3002 is screwed in position on the opposed pressing plate 3006.

For the effect that the Separating force that reaches hope descends, the device of this packing spring or replacement packing spring must be in series with operation dish spring 3004.The device that this means this packing spring or replacement packing spring produces resiliently deformable by dish spring 3004 applied forces.

To be described further the action principle that packing spring or packing spring substitute part in conjunction with the form of implementation in Figure 59 and 60 and the characteristic curve in Figure 76,77 plotted curve now.

The part area of the power that curve 3035 expressions in Figure 76 are relevant with the variation of dish spring 3004 inclinations, this power is the total axial force that is applied on platen 3003 by dish spring 3004.This part area 3050 is corresponding to the axial deformation of the annular matrix 3012 of pivoting support 3005 and the dish spring 3004 between radially outer on the platen 3003 supports.In part section 3050, also considered by supporting dish spring 3009 and when needing by other parts such as leaf spring 3015 applied forces, these power have been made the distortion of dish spring 3004 and having been supported or influence.The true power of dish spring 3004-stroke curve with dashed lines 3050a is illustrated among Figure 76.Be that in fact dish spring 3004 has the power-stroke curve higher than curve 3050.

Point 3051 representative mounting points of dish spring 3004 in the new clutch 3001 of a closure, just dish spring 3004 acts on the position of platen 3003 maximum impacting forces on corresponding mounting point.Point 3051 can move up or down along curve 3050 by the change of dish spring 3004 taper mounting point in new clutch.

Curve 3052 expressions are by the power of axially opening of packing spring section 3016 effects, and this masterpiece is used between two friction linings 3007 and acts on the platen 3003.This power of axially opening act on the contrary by dish spring 3004 be applied on the platen 3003 axially on.Advantageously be equivalent to put on the maximum, force of platen 3003 at least by dish spring 3004 by the maximum axial force that resiliently deformable produced of spring section 3016, and this power also can be big again, so that spring section 3016 also has the elasticity deposit when friction clutch 3001 is closed fully, promptly on a definite stroke, go back elastically deformable.When friction clutch 3001 separates, 3016 unloadings of spring section, and through stroke 3053.On the corresponding stroke 3053 of axial displacement of this and platen 3003, kept the separation process of clutch 3001.Therefore must apply a less maximum separation power, this maximum separation power is not less than when having packing spring 3016 and mounting points 3051 corresponding maximum separation power.Surpassing point 3054 o'clock, friction lining 3007 is released, at this moment because the recession curve zone of dish spring 3004 makes also at the Separating force of effect has reduced significantly with respect to the power corresponding with point 3051.Till when dropping to its minimum value always or reaching the valley point 3055 of curve 3050 for the Separating force of clutch 3001.Required separation are risen again after surpassing minimum point 3055, and at this moment the separation stroke in the tip of the tongue 3010 zones guarantees in this wise: even Separating force also is not more than the supporting force that is produced by dish spring 3009 when surpassing minimum point 3055.This is necessary, because otherwise can when separation phase, form wear sensor 3037 undesirable rise and cause the adjustment of compensation device 3017 thus from the wear sensor 3020, the consequence that this will cause friction clutch to separate at least no longer fully, clutch can not be separated again under extreme case, promptly no longer may interrupt torque or power transmission by friction clutch.

Power-stroke curve that supporting dish spring 3009 has corresponding to curve among Figure 77 3057.The curve that this curve 3057 is produced when the unloaded position tapering changes and have a radial distance between two pivoting supports corresponding to dish spring shape parts 3009, this radial distance are equivalent to cover the distance between side pivoting support and the operation dish spring side pivoting support.Can see that by curve 3057 dish spring shape parts 3009 have springing stroke 3058, in fact the axial force that is produced by it on the trip keeps constant.The power that produces on this zone 3058 can be selected like this, and promptly during the operating life of friction clutch 3001, this power is all the time greater than the maximum separation power that occurs on dish languid point zone 3010.The supporting force that is produced by sensing spring 3009 is relevant with the lever ratio of dish spring 3004.Yet this lever ratio under most situation in 1 to 3 to 1 to 5 value, for some applicable cases also can be greatly some or smaller.Described dish spring lever ratio is equivalent to support radial distance between the supporting diameter of 3005 to two dish springs 3004 and 3009 and pivoting support 3005 ratio to the radial distance between the contact diameter of operation equipment, and this operation equipment is a separation support in the tip of the tongue 3010 zones for example.

The mounting point of dish spring shape parts 3009 is to select like this in friction clutch 3001: but its not only resilience in separating stroke, and on the direction of friction lining 3007, has a spring travel, the trip is equivalent to the axial adjustment stroke of platen 3003 on the direction of opposed pressing plate 3006 at least, this adjustment stroke be by on the friction lining and rubbing surface on wearing and tearing form.What meet the requirements is should guarantee on this spring travel of spring 3009: separate required power by the axial force that this spring 3009 acts on the dish spring 3004 greater than friction clutch.Simultaneously advantageously the minimum length that has of the zone 3058 of curve 3057 corresponding to the greatest wear stroke, preferably greater than this wearing and tearing stroke, because also can compensate location tolerance at least in part thus.

Using because the rising of platen 3003 when producing the leaf spring 3009 of precompressed effect, platen 3003 is pressed on the dish spring 3004 through these leaf springs 3009, thus also can be via the support of leaf spring 3009 generation separation processes.Also promptly superimposed with the power that produces by dish spring 3009 by the axial force of leaf spring 3009 generations.This plate spring component 3009 can be arranged between lid 3002 and the platen 3003 in this wise, i.e. increase along with friction lining 3007 wearing and tearing is also increased by the axial force that leaf spring 3009 acts on the operation dish spring 3004.For example can make in Figure 77 on the stroke 3058 thus and the axial force of therefore also being transmitted by leaf spring 3015 on the wear compensation stroke of regulating device 3017 has curve according to curve 3057b.So leaf spring 3015 produces along with the wearing and tearing of friction lining 3007 increase and becomes big return force and act on the operation dish spring 3004.If the curve according to curve 3057 is desirable now, then dish spring 3009 must be designed like this, even it has the characteristic curve corresponding to curve 3057c.

Should also be noted that operation dish spring 3004 is being pressed pivoting support 3005 the power storage for example dish spring shape parts 3009 also can have other power-stroke curve, promptly be different from the curve of Figure 77.With the power-stroke curve that causes this spring to produce in 3058 in the zone at least also be rise or descend.Importantly when every kind of situation, should guarantee, by this spring 3009 and when needing by other spring members, as leaf spring 3015 produce should be to the synthetic supporting force of operation dish spring 3004 greater than the Separating force that is used for friction clutch of adverse effect being arranged with this power.

Wearing and tearing of expression sensing ring 3720 in Figure 78, it is made up of two parts 3720a, 3720b at least, is provided with a spring 3738 at least on axial between them.This wearing and tearing sensing ring 3720 for example can be used for replacing the wearing and tearing sensing ring 3020 according to Figure 59, but the parts that wherein are adjacent must adapt with it.Constitute the parts 3720a of wear sensor 3720, holding device 3739 that 3720b can do to circularize and by the rivet form interfixes with certain axial distance.The spring assembly 3738 of the dish spring form that is clipped by rivet 3739 is being pressed these two rings 3720a, 3720b to make in the axial direction and is being separated from each other, but wherein, as stating, these two rings 3720a, 3720b are maintained on the predetermined axial distance L via rivet 3739.Ring 3720a has rising sloping platform 3723, this sloping platform for example with shell on opposed rising sloping platform interact, be similar in conjunction with Figure 59 to 66A described.This spring assembly 3738 combines with two parts 3720a, 3720b and plays the effect of a wear sensor, and the parts 3037 that its mode is similar to according to Figure 59 combine with parts 3020.Dish spring 3704 at least when relevant clutch separation to constituting as the parts 3720b application of force of annular, when separation process, make spring assembly 3738 pressurizeds thus.So just, the 3720 undesirable adjustment of wearing and tearing sensing ring have been avoided.After parts 3720b is through a predetermined axial stroke, the trip is for example corresponding to value L, the relative parts 3720a of parts 3720b forms axial restraint, availablely thus be similar to described mode in conjunction with Figure 59 to 66A, make dish spring 3704 axially mountings own on parts 3720b, can make thus with the sensing ring 3720 coefficient wear compensation rings (for example parts among Figure 59 3018) that wear and tear when dish spring 3710 further turns round, to unload by this dish spring.Therefore when the friction lining of friction clutch has has just worn and torn, the wear compensation ring is adjusted corresponding to sensing ring 3720 rotation just now of wearing and tearing.

In the form of implementation of the friction clutch shown in Figure 79 and 80 3801, regulating device 3817 is to be similar to the mode of form of implementation among Figure 73, be axially disposed between dish spring 3804 and the platen 3803, but be fixed on dish spring 3804 on the one side of lid 3802 as the elastic member 3837 of wear sensor here.The opposed rising sloping platform 3821,3822 that interacts with ring 3818,3820 rising sloping platform 3819,3823 and be located at the platen side is made of panel-like member 3803a, and it is supported by platen 3803.Be provided with hole 3803b between adjacent in a circumferential direction each the opposed rising sloping platform 3821 and/or 3822 of this panel-like member 3803, it can realize the air circulation between platen 3803 and the plate-like piece 3803a.This platen 3803 has the configuration of depression 3803c form simultaneously, and it makes the air circulation between plate-like piece 3803a and the platen 3803 become and may and guarantee that thus platen 3803 better cools off.

In order to realize the simple assembling of friction clutch according to the present invention, what meet the requirements is to be provided with to put forth effort the zone on wearing and tearing sensing ring and/or wear compensation ring, as rotating or the maintenance instrument, can make regulating device be transferred to the position of its withdrawal by this instrument, also promptly corresponding position with the new state of friction clutch.In form of implementation according to Figure 59, when making or assemble friction clutch 3001, as long as by an instrument wearing and tearing sensing ring has been forwarded on the position of its withdrawal, because also automatically make 3018 withdrawals of wear compensation ring by the rotation of wearing and tearing sensing ring 3020.On the position of this withdrawal, then with a Locking Device wearing and tearing sensing ring 3020 is fixed at least, after friction clutch being assembled on the opposed pressing plate 3006, this Locking Device is removed, adjustment ring 3017 is worked.Use similar mode, wearing and tearing adjustment ring and/or wearing and tearing sensing ring are lockable.

Another kind wear compensation device is remained on and the corresponding initial position of friction clutch new state on possibility be: between platen and the shell or between operation dish spring and shell a holding device is being set at least, it remains on the position that retracts or compress with respect to shell platen and/or extruding dish spring, and the position that the back is had on the opposed pressing plate is installed to corresponding to this relevant friction clutch at least in this position.Can between shell and the opposed platen or between shell and extruding dish spring run distance caging device for example be set, as folder or pad, they can avoid pushing the unallowed unloading of dish spring for this reason.

The friction clutch shown in Figure 81 4001 have a shell 4002 and with this shell anti-be rotationally connected but the platen 4003 that axially can move spacingly.Axially upward be pressed with an extruding dish spring 4004 at platen 4003 and between covering 4002, it can wind pivoting support 4005 revolutions by outer casing supporting, and to platen 4003 in the application of force on the direction of opposed pressing plate 4006, a this opposed pressing plate for example flying wheel is fixedlyed connected with shell 4002 through screw thread, and the friction lining 4007 of clutch disk 4008 is clamped between the rubbing surface of platen 4003 and opposed platen 4006.

Platen 4003 resists with shell 4002 through the leaf spring 4009 in circumferencial direction or tangent direction orientation and is connected rotationally.In this illustrated embodiment, clutch disk 4008 has so-called packing spring section 4010, it guarantees when strigil 4001 engages torque to be increased gradually, and it can increase the axial force that acts on the friction lining 4007 in restricted axial displacement on the direction that is harmonious each other by two friction linings 4007 gradually simultaneously.Yet also can use a kind of clutch disk, wherein in fact friction lining 4007 acts on the supporting disk axial stiffness.

In this illustrated embodiment, dish spring 4004 has an annular matrix 4004a who applies impacting force, radially inwardly extends to operation tongue 4004b by it.Dish spring 4004 is installed in this wise, it with its radially than exterior domain to platen 4003 application of forces, and rotate with radially changeing supporting 4005 than the inner region wraparound.

Pivoting support 4005 comprises two pivoting supports 4011,4012, and they are made of metal loop here, and axially keeps therebetween or clamping dish spring 4004.Pivoting support 4011 set on the face of the dish spring 4004 of platen 4003 on the direction of shell 4002 by power storage 4013 application of forces.This power storage 4013 is to constitute by a dishful of spring or by the parts 4013 of a dishful of spring class, it is bearing on the shell 4002 with its radially outward edge zone 4013a and with inner section 4013c radially pivoting support 4011 is pressed in operates dish spring 4004, and thus in the application of force on the axial direction of shell 4002.Set dish spring 4013 has an annular matrix 4013b between platen 4003 and operation dish spring 4004, extends radially inwardly to tongue 4013c by its inward flange, and this tongue then is bearing on the pivoting support 4011.Radially outer at matrix is configured to carriage 4013a, and it interacts with the support region 4014 that is gone out by shell 4002 straight formings.Between the support region 4014 of dish spring base part 4013 and carriage 4013a, form a kind of bayonet coupling or latch, so that at first axially compacted and make its radially exterior domain or after carriage 4013a radially is placed on the support region 4014 at dish spring base part 4013, again by dish spring base part 4013 relatively the corresponding carriage 4013a that makes parts 4013 that rotates of shell 4002 contact with support region 4014 formation.

On shell 4002, be fixed with in order to prevent to operate the centering part of the axially extended shaft of rivet form that dish spring 4004 rotates, each this parts all has an axially extended bar 4015a, extends in the breach that it axially sets between two adjacent dish languid 4004b.

This dish spring base part or dish spring 4013 constitute sensing spring, and it can produce basic at least near constant power on a predetermined working stroke.In case the plate spring component 4009 between shell 4002 and platen 4003 produces axial force, this power is just with superimposed by the axial force of sensing spring 4013 effects.Under the situation of the plate spring component 4009 that is installed in friction clutch 4001 like this, be that it makes platen 4003 towards shell 4002 or under the situation of the dish spring 4004 direction application of forces, by plate spring component 4009 power that applies and the power addition that applies by sensing spring 4013, so just constituted a so-called sensing that acts on the dish spring 4004 and made a concerted effort.Also must consider the power that is not applied during sensing spring 4013 all the time in design.The axial force that is applied by plate spring component 4009 is superimposed upon similarly by dish spring 4004 and puts on the power of platen 4003, therefore work as plate spring component 4009 and be subjected under the situation of precompression from the direction that clutch disk 4008 rises at platen 4003, the axial clamping force that is acted on the friction lining 4007 by platen 4003 compares the little power by the leaf spring effect of axial force that is acted on platen 4003 by dish spring 4004.The clutch separation power of resistant function on the tip of the tongue 4004c of making a concerted effort by leaf spring 4009 and sensing spring 4013 effects, wherein at least when friction lining 4007 discharges, be similar to the maintenance balance with joint efforts at least in power that produces on the pivoting support 4011 and the sensing that acts on this pivoting support 4011 by Separating force.Separating force is should be understood to, when friction clutch 4001 operations, act on the tip of the tongue 4004c of dish spring clutch or the power on the separator levers.This Separating force can change from the separation stroke of the tip of the tongue zone 4004c.

The pivoting support 4012 of shell side is bearing on the shell 4002 via a regulating device 4016.This regulating device 4016 guarantee when pivoting support 4011 and 4012 towards platen 4013 directions or towards opposed pressing plate 4006 direction axial displacements the time, do not forming any undesirable gap between pivoting support 4012 shells 4002 or between pivoting support and the dish spring 4004.Also guarantee when actuating friction clutch 4001, not form any undesirable invalid or idle stroke thus, obtained the operation that best efficient reaches the friction clutch 4001 that therefore improves thus.Pivoting support 4011 and 4012 axial displacement be the rubbing surface of platen 4003 and opposed pressing plate 4006, and friction lining 4007 produce when axially wearing and tearing occurring.Automatic adjustment working principle to pivoting support 4005 will be described further in conjunction with the plotted curve according to Figure 84 to 86.

Regulating device 4016 comprises the spring-loaded adjustment component of annular component 4017 forms, and it has the rising sloping platform 4018 that stretches in a circumferential direction and axially go up rising, and the latter is distributed on the circumference of these parts 4017.This adjustment component 4017 is installed in the clutch 4001 in this wise, i.e. its sloping platform 4018 4002a at the bottom of the shell that rises.Be a pivoting support 4012 that is made of metal loop on the face of the adjustment component 4017 of carrying rising sloping platform 4018, it is concentrically positioned in the seat of groove shape.

In this illustrated embodiment, adjustment component 4017 for example is that a kind of heat resistant plastice is made by plastics, and it also can additionally be strengthened with fiber.Available thus simple mode makes adjustment component 4017 as manufactured come out of spray casting die.This adjustment ring 4017 will be used in that the regional 15a that extends axially of equally distributed rivet comes the center on the circumference.

Adjusting ring 4017 its rising sloping platforms 4018 is bearing on the opposed rising sloping platform 4019 of die casting in 4002a at the bottom of the shell.The lid die castings that constitutes opposed rising sloping platform 4019 is to constitute like this, and promptly it always constitutes a vent hole 4020a on the sense of rotation of clutch 4001.By a kind of like this configuration, when rotating, clutch 4001 make the parts that constitute clutch 4001 produce better cooling, and the adjustment ring 4017 that is made of plastics is cooled off better.The die castings of this lid also is to construct like this, and promptly it plays a kind of forced air circuit effect that makes by in lid 4002 clutch space that limit.

Sloping platform 4018,4019 is in a circumferential direction with regard to its length and to be provided with regard to the angle be to constitute like this, promptly adjust ring 4017 and can rotate an angle relative to shell 4002 at least, its occurring wear on guaranteeing the rubbing surface of platen 4003 and opposed platen 4006 during the whole operating life of friction clutch 4001 and on the friction lining 4007 compensates.This offset angle calmly can be in the magnitudes of 8 to 60 degree on the design of rising sloping platform, are preferably in the level of 10 to 30 degree.The tilt angle of sloping platform 4018,4019 can be in the scope of 3 to 12 degree.This angle is to select like this: press formed frictional force will stop slip between these two sloping platforms 4018,4019 each other mutually by rising sloping platform 4018 and opposed rising sloping platform 4019.

Adjusting ring 4017 is spring loaded in a circumferential direction, and be to adjust the application of force on the direction, this direction just makes in the slip on the opposed sloping platform 4019 by sloping platform 4018 and adjusts ring in the direction that produces axial displacement on the direction of platen 4003, this means that its effect leaves on the direction of shell section 4002a radially in the axial direction.

As can seeing in conjunction with Figure 82, the spring-loaded of this adjustment ring 4017 guarantees by each helical spring 4020, and they extend on the circumferencial direction of lid 4002 and be pressed in and adjust between ring 4017 and the shell 4002.Three such helical springs 4020 preferably are set, and they are evenly distributed on the circumference.Each helical spring 4020 is admitted or is mounted on the sheet 4021, and this sheet and clutch housing 4002 constitute one.This sheet 4021 be by the sheet material of lid by configuration example as the breach 4022 of going out a U-shaped and moulding.This sheet 4021 stretches with seeing arc ground or tangent direction and preferably is at least approx on the axial height identical with the lid of direct neighbor zone at circumferencial direction.The width of this sheet 4021 is to set like this, and promptly it not only leads to cover helical spring 4020 thereon diametrically but also in the axial direction.Adjustment ring 4017 by spring 4020 application of forces on the adjustment direction has radially inner profiled member or carriage 4023 on the circumference within it, and its inner radial has a fork or a U-shaped spare 4024 in axial orientation.Each U-shaped spare 4024 has the tenon 4025 of two axles, and they prop up sheet 4021 round a spring guiding from both sides.These two tenons 4025 axially penetrate or pass the breach 4022 on the shell 4002 for this reason.These tenons 4025 are by adjusting spring 4020 application of forces.

When friction clutch 4001 new states, the axial raised portion that constitutes rising sloping platform 4018 and the opposed rising sloping platform 4019 axial farthest of working in coordination this means to make ring 4017 and make pivoting support 4005 also move to the farthest on the direction of lid end 4002a thus.

Friction clutch 4001 has an additional power storage 4026, and it is made of dish spring shape parts.These dish spring shape parts 4026 have an annular matrix 4027, extend radially inwardly out the carriage 4028 of ligule from this matrix.These dish spring shape parts 4026 axially are arranged on and cover between end 4002a and extruding dish spring or the operation dish spring 4004, and the latter keeps with being positioned relatively.Tongue 4028 is in axially annular matrix 4027 bendings relatively in this wise for this reason, promptly this tongue axially passes the hole 4029 between the tongue 4004b that is located at dish spring 4004 in a circumferential direction, and with its radially aduncate regional 4030 reverse grip on the pivoting support 4011 that constitutes by a metal loop.The axial orientation of dish spring shape parts 4026 relative dish springs 4004 is to realize by the spring assembly 4031 of similar leaf spring, this spring assembly is connected with dish spring 4004 axial restraint ground and to the zone 4030 of tongue 4028 application of force axially, make dish spring shape parts 4026 thus, the annular pivoting support 4011 that dish spring 4004 reaches between the end regions 4030 that axially is located at dish spring 4004 and tongue 4028 is compacted in the axial direction.Tongue 4028 is arranged in a circumferential direction with respect to the tongue 4013c of sensing spring 4013 with staggering.

As appreciable from Figure 82, dish spring shape parts 4026, dish spring 4004 and annular pivoting support 4011 are combined into a prefabricated unit by means of leaf-spring-like spring members 4031, and it can be used as pre-assembled module and is encased in shell or the lid 4002 when friction clutch 4001 assemblings.The position of in Figure 83, representing not stressed dish spring 4004 relative dish spring shape parts 4026.

Can find out from Figure 81, even be installed at friction clutch 4001 under the state of opposed pressing plate 4006 and between dish spring 4004 and dish spring shape member 4026, have an axial distance or gap 4032, dish spring 4004 at this moment be in the corresponding position of the jointing state of friction clutch 4001 in, and dish spring shape parts 4026 are in its lax position.The radially distance between the exterior domain 4023 in these two annular spring matrix 4004a and 4027 must be set like this, promptly when the separation process of friction clutch 4001, the dish springs 4004 that support 4005 rotations are changeed in wraparound could be to dish spring shape parts 4026 application of forces behind an angle of revolution or separation stroke, and the trip is equivalent to the release of clutch disk 4008 at least approx.The release of clutch disk 4008 or friction lining 4007 is interpreted as a kind of serviceability of friction clutch 4001, in fact no longer be clamped at friction lining 4007 under this state between the rubbing surface of platen 4003 and opposed platen 4006, also be the state of this friction clutch 4001, in fact can not transmitting any torque to clutch disk 4008 under this state by opposed pressing plate 4006.Packing spring section 4010 is unloaded in the serviceability of this friction clutch 4001.This distance 4032 is preferably set in this wise, promptly after friction lining discharges soon, dish spring 4004 just forms with dish spring shape parts 4026 and contacts.These dish spring shape parts 4026 are as counterbalance spring, and it makes the Separating force curve of the friction clutch 4001 after clutch disk 4008 discharges be adapted to desirable stroke-force characteristic.Respective design by counterbalance spring 4026 can make Separating force curve " linearization " in the residue separation stroke after friction lining 4007 discharges, this means that in fact the Separating force that is applied can keep constant on this remaining separation stroke, perhaps on the trip at least the variation of Separating force can reduce in fact.

To further specify the working principle of above-mentioned friction clutch 4001 in conjunction with characteristic curve represented in the plotted curve according to Figure 84 to 86 now.

Curve 4033 expression among Figure 84 and the tapering of dish spring 4004 change relevant and consider the synthesis of the axial force curve that the power that acted on by plate spring component 4009 obtains, and obtain during this distortion that is dish spring 4004 between two supporting tongues, the radial distances of these two supporting tongues are equivalent to pivoting support 4005 and the radial distance between the axial external support diameter 4003a on the platen 4003.On the horizontal ordinate be stroke to axial between these two supports, and on ordinate expression by making a concerted effort that dish spring 4004 and plate spring component 4009 are produced.Point 4034 representative mounting points of dish spring 4004 in the clutch 4001 of closure, just dish spring 4004 acts on the position of the maximum impacting force of platen 4003 on corresponding mounting point.Point 4034 can move up or down along curve 4033 according to the change of dish spring 4004 taper mounting points.

Curve 4035 expressions are by the power of axially opening of packing spring section 4010 effects, and it acts between two friction linings 4007.In this curve, also comprise the active force that all springs of same function are arranged with packing spring, Gai elasticity for example, the elasticity of pivoting support or the elastic device between dish spring and platen supporting or the elasticity of analog when needing.It is opposite by the responsive to axial force that dish spring 4004 is applied on the platen 4003 that this axially opens power.Advantageously for the required axial force of the resiliently deformable of the maximum possible of spring section 4010 at least corresponding to acting on power on the platen 4003 by dish spring 4004 in the jointing state of friction clutch 4001.Spring section 4010 unloadings when friction clutch 4001 separates, and through stroke 4036.On this stroke corresponding 4036 with the corresponding axial displacement of platen 4003, kept the separation process of clutch 4001, this means, promptly must apply the little maximum separation power of mounting points 4034 corresponding maximum separation power when not having packing spring section 4010.Surpassing point 4037 o'clock, friction lining 4007 is released, and at this moment because the characteristic curve zone of dish spring 4004 descends gradually, makes also and reduces significantly with respect to point 4034 pairing power at the Separating force that acts on.The Separating force that is used for clutch 4001 when not having counterbalance spring 4026 will drop to till the point 4038 that reaches on the horizontal ordinate always.On detaching direction, put the axial force that then produced at 4038 o'clock the direction transformation has taken place by dish spring 4004 above this, so that automatically on detaching direction, overturning, and to the minimum value of sinusoidal shape characteristic curve 4033 or the automatic convergence of direction of valley point 4038a or 4039a above 4038 o'clock dish springs 4004 of point.Surpass point 4038 o'clock on detaching direction, the power that is applied by dish spring 4004 becomes negative, and therefore friction clutch 4001 automatically stays open when not having counterbalance spring 4026.When in the separation process of friction clutch 4001, surpassing minimum point 4038a, drop to point 4039 on the axis of abscissa again by the negative power of dish spring 4004 effects till.On detaching direction, surpass the power that point produced by dish spring 4004 at 4039 o'clock and just becoming again, and when reaching 4039a, be used to stretch the required power of dish spring 4004 and put 4037 set power and be consistent.

The plan-position that the plotted curve of Figure 84 has further been put down in writing the plan-position 4033a dish spring 4004 of dish spring 4004 is to represent with each deformation position of dish spring 4004, on these positions, each deformation position of the matrix 4004a of cyclic spring is represented, on these positions, the matrix 4004a of cyclic spring with perpendicular to the plane parallel of dish spring rotating shaft move.

As from by point 4037,4038,4038a, 4039,4039a can see the line segment of process, during no secondary spring 4026, make friction plate 4007 have the substantial variations of power after discharging in the Separating force distribution curve by axially mentioning platen 4003.The variation of this power is harmful to.Because in this zone, will accurately distribute particularly to change and distribute that to engage with separating stroke be very difficult according to the different power in minimum value 4038 (being negative value herein) both sides.This difficulty is to foot-operated transmission and utilize the friction clutch of actuating motor transmission all to exist equally.In order to overcome this defective and in order on the required ventilation stroke 4040 of platen 4003, to keep the Separating force distribution curve of expection, and being provided with dish spring type parts 4026, these parts are at the power-stroke characteristic curve (considering that it is at support distances on the dish spring 4004 and the distance relation between dish spring 4104 supports on platen projection 4003a and the pivoting support 4011,4012) that has among the described embodiment shown in dotted line 4041.Shown in Figure 84, dish spring 4004 and dish spring type parts 4026 have reverse power-flight distribution curve in ventilation stroke 4040 at least.In described embodiment, dish spring type parts 4026 only work to the part area 4042 of ventilation stroke 4040.The ventilation stroke should be understood as such stroke, promptly the trip is when driving clutch, and after friction pad 4007 discharged, platen 4003 was at the stroke of axially also passing by.Shown in Figure 84, in clutch 4001 separating process, make dish spring type parts 4026 after surpassing the point of release 4037 of friction pad 4007, begin action again.Represent by superposeing or adding the power distribution curve that spring characteristic curve 4033 and 4041 forms with curve 4043.This distribution curve 4043 begins at point 4044 places.

The initial point 4044 that is suitable for dish spring type parts 4026 is to determine according to the axial distance between dish spring 4004 external margins and the dish spring type parts 4026 outer radial zones 4032.Ventilation stroke 4040 is like this designs, promptly reach when making the stroke that friction clutch 4001 separates fully when it, with the end points 4045 corresponding Separating forces of ventilation stroke 4040 less than with put 4037 corresponding Separating forces.As also will describing in detail, this design mainly is for fear of the adjustment that occurs violating original idea in regulating mechanism 4016.

Requiredly in the contact diameter 4004d zone, corresponding the tip of the tongue 4004c zone be used for separating stroke and comparing of friction clutch 4001, the corresponding increase of the lever transmission ratio of its dish spring 4004 supporting from the axially displaced stroke 4046 of the available platen 4003 of Figure 84 with for example clutch separation.This dish spring velocity ratio or lever transmission ratio are corresponding to the proportionate relationship of the radial distance between pivoting support 4005 and operation or the contact diameter 4004d and pivoting support 4005 and the radial distance between the support diameter 4003a in the middle of dish spring 4004 and the platen 4003.In most of the cases the order of magnitude of this power transmission ratio is 3: 1-5: 1, but also can be greater or lesser in some application.In the embodiment shown in Figure 81, the order of magnitude of this velocity ratio is 4.2.

Separating force distribution curve in the ventilation stroke 4040 relevant with the operation diameter 4004d in the 4004c zone, the tip of the tongue district reduces than the curve shown in Figure 84 to some extent according to above-mentioned velocity ratio equally.

When curve 4047 was illustrated in friction clutch 4001 and separates in Figure 84, the retraction stroke 4036 by spring part 4010 was added in the power in the zone of the contact diameter 4003a between platen 4003 and the dish spring 4004.It is poor with the power distribution curve of the power distribution curve 4035 of spring part 4010 that curve 4047 is equivalent to the line between 4034 and 4037 a little 4033.Power distribution curve in the operation diameter 4004d zone of the dish languid 4004b of portion is compared with the power distribution curve 4047 among Figure 84, lever transmission ratio according to dish spring 4004 dwindles, and still required axial stroke is compared with the retraction stroke of spring part 4010 and wanted the corresponding increase value relevant with velocity ratio in operation diameter 4004d zone.In according to the designed friction clutch of Figure 81-84, can only make operation dish spring or 4004 revolutions of main dish spring by a part of separating stroke, and arrive secondary spring or counterbalance spring 4026 and contact with it up to the outer rim of dish spring 4004.After this, main dish spring 4004 turns round jointly with counterbalance spring 4026, the curve 4043 that the power-flight distribution curve mutual superposition of two springs and formation is simultaneously synthesized, and this curve will extend in the part area of ventilation stroke 4040 at least.Shown in Figure 84, can select the minimum force value 4038a of dish spring 4004 very little, but also can get negative value, thereby minimum value 4038a is positioned under the horizontal ordinate.Dish spring 4004 has constituted a so-called bumping type spring in these cases, and this spring has the position of a tension, not influenced by external force at this position upper spring.Counterbalance spring 4026 at least with the minimum value 4038a place adjacent areas of main dish spring 4004 in the generation effect.

Required power increased when counterbalance spring 4026 can cause making in ventilation stroke 4040 friction clutch 4001 to separate, therefore compare with the variation that occurs in the characteristic curve district of the power-flight distribution curve 4033 of the dish spring 4004 that in ventilation stroke 4040, extends, can greatly reduce the variation that occurs in the Separating force distribution curve.

As the spring 4013 of force transducer have with Figure 85 in line 4048 corresponding stroke-Li distribution curves.Formed curve when characteristic curve 4048 is equivalent to dish spring type parts 4013 and changes from the decompression position to the gradient, that is to say this moment of run-off the straight between two rotary supports with radial distance, its radial distance equals rotary support or supports radial distance between 4011 and 4014.

Operation dish spring 4004 forms by a plurality of power additions to total power that the pivoting support 4012 that covers side applies when friction clutch 4001 separates and in clutch disk 4008 release backs, if these are advocated by plate spring member 4009, the Separating force that exists on sensor spring 4013 and the operation dish spring 4004 in operating area 4004d produces.Plate spring member 4009 can place between lid 4002 and the platen 4003 like this, and promptly along with the increase of rubbing cushion 4007 wearing and tearing with in the stroke 4046 that clutch 4001 engages, the axial force that is formed on operation dish spring 4004 by leaf spring 4009 becomes big.So in the stroke shown in Figure 85 4049 and in the wear compensation stroke of controlling device 4016, have the distribution of the rising shown in line 4045 by the axial force of leaf spring 4009 generations.Can also know that from Figure 85 along with the increase of sensor spring 4013 press-bending amounts, the reposition force that is produced on platen 4003 by leaf spring 4009 also increases thereupon, this reposition force also acts on the operation dish spring 4004.By the power distribution curve addition shown in characteristic curve 4050 and the dish spring characteristic curve having been formed synthetic power distribution curve 4051, this power from axial action on dish spring 4004, and at dish spring 4004 on the direction of rotary support 4012 pressurizations of lid side.Can also reduce the supporting force or the supporting force distribution curve that in stroke 4049, form at least by sensor spring 4013 by the corresponding precompression of leaf spring 4009.In described embodiment, sensor spring 4013 has that reduce or negative stroke-Li distribution curve in stroke 4049.Reduce to fill up spring elasticity and/or will fill up the middle form of spring spare embedding friction pad the Separating force increase that is occurred is proceeded to the small part compensation by plate spring member 4009 being carried out suitable layout and designing to utilize equally, wherein when dish spring 4004 is shifted, on the direction of power 4051 on the sensor slight increase is arranged at opposed platen.Can guarantee thus, in fact dish spring 4004 is remained in the clutch 4001 of closure on identical operation point 4034 or the identical working area 4046, so can in fact produce the pressure of approximately constant at least at dish spring 4004 during the friction clutch operating life on platen 4003.In addition, in design during friction clutch especially when sensor spring 4013 and/or leaf spring 4009, must consider by acting on adjustment spring 4020 on the adjustment piece 4017 that form and to sensor spring 4013 and/or leaf spring 4009 reactive total axial forces.

When having the friction clutch of leaf spring 4009 of normal precompression, design must consider that also the precompression of leaf spring 4009 can influence the axial force that platen 4003 produces on friction pad 4007.This just means that when the precompression of leaf spring 4009 is added on the direction of operating dish spring 4004, the pressure that is produced by dish spring 4004 will reduce a same big amount of the precompression with leaf spring 4009.Can also form the synthesis pressure distribution curve for platen 4003 or friction pad 4007 in this friction clutch 4001, this curve is that the stack by the distribution curve of stress of the pressure distribution curve of dish spring 4004 and leaf spring 4009 constitutes.Suppose that from the characteristic curve 4033 shown in Figure 84 in view of the working area 4046 of clutch 4001 are the distribution curves of making a concerted effort that formed by operation dish spring 4004 and precompression leaf spring 4009 under the new state of friction clutch 4001, reducing along with distance between platen 4003 and the opposed platen 4006 so, for example by the pad wearing and tearing, and because along with the increase leaf spring 4009 that weares and teares produces countertorque on dish spring 4004, and synthetic distribution curve is moved towards reducing direction.This opposing torque is to form owing to pivoting support 4005 and the radial distance between the loading diameter 4003a in the middle of operation dish spring 4004 and the platen 4003.Design during friction clutch particularly importantly, the increase of the Separating force that the increase that preferably makes leaf spring 4009 pressure that cause because of cover plate wearing and tearing produces in control panel 4004d under identical pad abrasion condition less than (equaling at the most), this Separating force makes sensor spring 4013 produce required continuous revolution when adjusting.In addition, under the state that friction clutch engages, platen 4003 acts on pressure on the friction pad 4007 and the friction plate power that the dish spring produces when discharging and all reduces on rotary support 4011.Therefore can not adjust fully, because put 4034 and 4037 to minimum value direction generation displacement.

Leaf spring 4009 and/or spring 4013 has a springing stroke 4049 on the distribution curve with joint efforts among Figure 85, and the axial force that occurs in the trip keeps constant substantially or preferably slightly raises.Therefore should be chosen in the power that forms in the zone 4049 like this, promptly make this power be approximately equal to the Separating force with Figure 84 mid point 4037 corresponding clutches at least.With compare with the power of point 4037 corresponding dish springs 4004, total supporting force that sensor spring 4013 and leaf spring 4009 form reduces by the lever ratio of dish spring 4004.

The rigging position of dish spring type parts 4013 in friction clutch 4001 is to select like this, promptly this position should be able to guarantee to move an axial elasticity stroke on friction pad 4007 directions in the zone of pivoting support 4005, the trip at least should with adapt at the axial adjustment stroke of platen 4003 on opposed platen 4006 directions, adjust stroke and mainly be because the friction pad of friction surface wearing and tearing weares and teares produces.At least be approximately linear zone 4049 in the characteristic curve 4051 and preferably can have, because can partly compensate location tolerance so at least than the bigger length of above-mentioned wearing and tearing stroke.

In order when friction clutch 4001 separates, to make friction pad 4007 keep a point of release 4037 in fact constant or that determine, can between friction pad 4007, use double-deck arc-shaped pad spring, or paired single reed back-to-back is arranged to one fills up spring, wherein each also can have the axial precompression of appointment each other to reed.Can realize by means of the elastomeric precompression that is located between the friction pad, eliminate or compensate the embedding loss that reed during operation occurs at least basically on the friction pad back side.Should be understood as such loss with embedding loss, this loss is owing to causing on the back side that the sheet spring is embedded into pad.Proper is that making the elastomeric precompressed amount that is located between the friction pad is the 0.2mm-0.6mm order of magnitude.By the axial decompression stroke between two friction pads 4007 of suitable qualification or by a definite and elastomeric minimum precompression that between friction pad, work, can further realize, at least when friction clutch 4001 separates, in the definite stroke in Figure 84 by the elastomer that is provided with between the friction pad with platen 4003 to pusher.For the stroke 4036 that keeps determining, can be by a suitable bounding means in the axial stroke between the restriction friction pad on decompression direction of filling up spring 4010 or the compression aspect.Can use those pad springs relevant, for example disclosed the sort of pad spring in as the patent application P4206880.0 that clearly quotes the application's theme as proof with optimal way of the present invention.

For the optimum Working that guarantees friction clutch 4001 or guarantee the optimum Working of the adjustment that the wearing and tearing to friction pad compensate automatically, proper is, from the Separating force distribution curve 4052 shown in Figure 86, make by filling up spring 4010, sensor spring 4013 only at least wants more bigger or at least equal with leaf spring 4009 comparing with the Separating force of in operating area 4004d dish languid point 4004c being firmly grasped and change in the stroke in separating of Figure 86 with joint efforts of generation on the dish spring 4004 by sensor spring 4013 by friction pad with leaf spring 4009 with joint efforts and after mentioning platen 4003 then what produce on the dish spring 4004.

Up to the present observation is the mounting point at a completely specified dish spring 4004, and and be provided with the wearing and tearing of considering on the friction pad 4007.

Under the situation that particularly friction pad 4007 axially weares and teares of axially wearing and tearing, the position of platen 4003 produces displacement to the direction of opposed platen 4006, therefore produce changes in pitch therefrom and be formed on the pressure that produces by the dish spring under the jointing state of friction clutch 4001, and this pressure is increase trend.This variation makes invocation point 4034 move to the direction of point 4034 ', moves and put 4037 directions to point 4037 '.This variations disturb the equilibrium of forces that when clutch 4001 separates, exists in back rotation support 4011 zones between operation dish spring 4004 and sensor spring 4013 at first.The dish spring that causes owing to friction pad wearing and tearing also makes the distribution curve of Separating force to the direction displacement that increases to the pressure increase of platen 4003.Forming the Separating force distribution curve therefrom is with dashed lines 4053 expressions in Figure 86.Because the Separating force distribution curve raises, so in the separation process of friction clutch 4001, the total axial force that is produced on dish spring 4004 by sensor spring 4013 and leaf spring 4009 is overcome, make the bending of sensor spring 4013 in the about axial stroke of the region generating of pivoting support 4005 like this, in fact this be equivalent to the wear extent of friction pad 4007.In the 4013 press-bending stages of sensor spring, dish spring 4004 is around the loading zone 4003a revolution of platen 4003; Therefore thereby the gradient that makes the dish spring changes and make in the spring energy stored or the torque of storage and the power that is produced on rotary support 4011 or sensor spring 4013 and on platen 4003 by dish spring 4004 as described above change.As seeing from the relation shown in Figure 84, the power that these variations cause dish spring 4004 to produce reduces.These change last till always make the dish spring in the zone of rotary support 4011 till the steering force that produces on the sensor 4013 and sensor spring 4013 and leaf spring 4009 formed reaction forces reach balance.This means, the plotted curve mid point 4034 ' shown in Figure 84 and 4037 ' and shift to a little 4034 and 4037 direction once more.After reaching this balance once more, platen 4003 can be mentioned from friction pad 4007 once more.In the stage of in friction clutch 4001 separation processes, wearing and tearing being adjusted, the adjustment component 4017 of controlling device 4016 rotates by precompression spring 4020, rotary support 4012 is moved with respect to the wearing and tearing of friction pad, has so just guaranteed to make the pivoting support 4005 of dish spring 4004 to keep no gap.After adjustment process finished, the Separating force distribution curve met the line 4052 among Figure 86 again.The axial stroke of line 4054 among Figure 86 and 4055 expression platens 4003, it is corresponding with Separating force-stroke curve center line 4052 and 4053.

In practice, above-mentioned adjustment all is continuously or takes place in the very short time lag, so bigger some displacement and the characteristic curve displacement represented in curve in order to understand the present invention better normally can not go out.

Duration of work by friction clutch 4001 can change some performance parameters or operation point.So for example because friction clutch turns round inappropriate meeting that pad spring 4010 is produced is overheated, and cause the pad spring thus or pad spring section 4010 is sunk or axial elasticity reduces.Yet, the characteristic curve 4033 by suitable design dish spring 4004 and/or the characteristic curve 4050 of leaf spring 4009 and/or the distribution curve 4048 of sensor spring 4013 done suitably to adjust can guarantee that friction clutch has the reliable ability of running.

Can also arrange the torque transfer device 4009 between shell 4002 and platen 4003 like this, that is, make it when friction clutch 4001 separates, can produce the required whole power of axially mounting.Under the situation of such design torque transmitting set 4009, can also save dish spring 4013.Therefore must arrange like this to make it to have such stroke-Li distribution curve by torque transfer device 4009, this curve can guarantee that at friction clutch 4001 duration of works wear compensation mechanism 4016 has infallible adjustment function at least.

The clutch device that has friction clutch 4101 that Figure 87 described has the structure close with the clutch device shown in Figure 81.The friction pad 4107 of clutch disk 4108 is with axial compression between the rubbing surface of the rubbing surface of the opposed platen 4106 that is made of flywheel and platen 4103.Main dish spring 4104 is pressed between clutch outer member 4102 and the platen 4103, and this dish spring is tiltably installed with respect to shell 4102 on pivoting support 4105.When clutch 4101 separated, the rotary support 4111 of axially support dish spring 4104 can directly be made of the dish spring type parts 4113 that use as the sensor spring.Between shell 4102 and dish spring 4104, make it produce axial force on dish spring 4104 dish spring type parts 4113 axial compression, this power is opposite with the Separating force direction that acts in the loading zone 4104d of dish languid point 4104c.Be provided with band between dish spring 4104 and the shell 4102 and adjust the controlling device 4116 of ring 4117, the adjustment ring can rotate and can adjust on the direction by at least one spring 4120 loading with respect to shell 4102.Controlling device 4116 with Figure 81 in the same mode of controlling device 4016 play a role, so, can consult the explanation of the relevant adjustment function that the wearing and tearing of friction plate 4107 are compensated among Figure 81.

In the structure of the friction clutch shown in Figure 87 4101, for the desired Separating force distribution curve of maintenance in the ventilation stroke of friction clutch 4101, and the auxiliary dish spring 4126 that will act on by platen 4103 after friction pad 4107 unloadings is arranged on the radially inner side of pivoting support 4105.Therefore, comparing the material that has in fact reduced as the secondary spring 4126 of counterbalance spring with the radial outside that secondary spring 4026 is arranged on rotating support 4005 in the embodiment shown in Figure 81 expends.

Secondary spring 4126 is axially disposed between adjustment ring 4117 and the dish spring 4104.Secondary spring 4126 has an annular matrix 4127, has radially support 4128 on the periphery of matrix, and support is distributed on the circumferencial direction of matrix 4127 and axially compresses in the zone of pivoting support 4105 or be clamped in and adjusts between ring 4117 and the dish spring 4104.

As seeing from the first half of Figure 87, auxiliary dish spring 4126 has the inboard radially-protruding tongue 4122 to matrix 4127, tongue is such curved shape in the axial direction, promptly when friction clutch 4101 is in jointing state, tongue passes vertically by the hole 4129 that is provided with in the middle of the dish languid 4104b, and locatees backward with axially spaced-apart or the gap determined at the dish spring 4104 that radially bends in the relative tongue 4104b zone that petiolarea 4130 forms.

Lower half portion of Figure 87 represents to be used to adjust the another kind of modification structures of determining gap 4132.Be provided with in this modification structures along the single riveting parts 4131 of the circumferential distribution of dish spring 4104, the bar of this riveting parts extends and has one towards the direction of shell 4102 bottom 4102a and acts on block on the auxiliary dish spring 4126 by what termination 4132 constituted.Auxiliary dish spring 4126 has radially inner fork-shaped support 4126a, this support be enclosed in riveting parts 4131 bar around.

The advantage that embodiment possessed shown in Figure 87 is not need to fix auxiliary dish spring 4126 with additional parts in friction clutch.In the embodiment shown in Figure 81, then to address that need with parts 4031 and fastening piece for this reason.Auxiliary dish spring 4126 always keeps being held in friction clutch 4101, and is in main dish spring 4104 and adjusts and encircle between 4117 when the jointing state of clutch 4101.When friction clutch 4101 separated, auxiliary dish spring 4126 can be compressed by main dish spring 4104 after exceeding gap 4132.Therefore, the radially outer of auxiliary dish spring 4126 is bearing on the main dish spring 4104 in pivoting support 4105 zones and radially inner side is bearing on the loading zone that is located in the dish languid portion 4104b zone, the supporting region 4130 of this loading zone and auxiliary dish spring 4126 or 4126a acting in conjunction.

It is very simple by auxiliary dish spring 4126 is set to guarantee the assembly process when auxiliary dish spring 4127 is reliably pressurizeed simultaneously.Figure 87 represents that auxiliary dish spring 4126 is on the lax position.Can be that the joint and clinging type structure also can be axial inserting turning linkage structure between the axial general construction of the auxiliary dish spring 4126 shown in Figure 87 upper half part and the main dish spring 4104.For this reason, make the tongue 4122 of axioversion pass the opening of corresponding formation in the dish languid portion and its of immigration be had in the slit of small circumferentially extending, axially go up facing on the position of dish spring 4104 supporting regions thereby loading zone 4130 is in by the rotation between two dish springs 4104 and 4126.Dish spring 4104 and 4126 retaining mechanism not only opposite shell 4102 but also mutually positioning and guiding by bolt 4115 forms are installed in friction clutch 4101 on the position of dish spring 4104 and 4126.

With regard to the formation of the Separating force distribution curve of friction clutch 4101, auxiliary dish spring 4126 has played the effect the same with secondary spring 4026 among Figure 81, can consult the explanation to Figure 81 to Figure 86 to this.

Friction clutch 4101 has in the part speed range that can rotate when clutch 4101 is used at least makes the device that the counteractive supporting force of Separating force is increased.Can avoid thus because the disturbing factor that occurs when for example revolution raises causes producing inappropriate adjustment when friction clutch 4101 work.In friction clutch 4101, these devices are by centrifugal device, promptly by being located at moulding counterweight on sensor dish spring 4113 outer rims and constituting to the tongue of holding up 4156 towards the axis of orientation of lid 4102.In the clutch 4101 that rotates, owing to act on that centrifugal force on the tongue 4156 has produced on the power that a precompression that is superimposed upon by sensor spring 4113 self forms and with the power of its addition.The Separating force of the operation dish spring 4104 in rotary support 4111 zones is increased.Thisly on rotary support 4111, will increase with the raising of rotating speed by the additional power that form of tongue 4156.

In the speed range of determining, particularly under higher motor rotary speed, for example, may cause platen 4103 under the separated state of friction clutch, to produce axial vibration owing to the vibration of motor excitation occurs.Because platen 4103 produces axial vibration, so can temporarily platen 4103 be mentioned from main dish spring 4104 at least, therefore can temporarily reduce making a concerted effort on the sensor, because at this moment the axial force that is produced by leaf spring type torque transmitter 4109 no longer works to dish spring 4104.If there is not this centrifugal device 4156 to cause, when carrying out structural adjustment in order to make mechanism 4116 reach the target adjustment, make dish spring 4104 or act on Separating force on the dish spring 4104 and synthetic Separating force on the effect dish spring 4104 or sensor force between the situation of required power be interfered, and make supporting force drop to unallowed level, and cause clutch 4101 to carry out too early and unwanted adjustment thus.The operation point of dish spring 4104 is moved towards the minimum force value.Rotating speed type or centrifugal force type device by tongue 4156 forms can compensate the disturbing factor of rotating speed.As mentioned above, can realize like this that the power that additional support power and sensor spring 4113 and/or plate spring member 4109 is produced by rotating speed structure or centrifugal force structure acts on side by side.

Friction clutch 4201 shown in Figure 88 A has constituted a so-called draw-off type friction clutch.The radial outside of dish spring 4204 is bearing on set between the radial portion 4202a of shell 4202 and the dish spring 4204 wear compensation ring 4218.Further inside zone is to projection 4213 application of forces of platen 4203 on the dish spring 4204.Be provided with wear sensor 4237 with a side that platen 4203 deviates from mutually on the dish spring 4204, this sensor by 4204 supportings of dish spring and with the dish spring by the clamping interlocking.Therefore the wear sensor 4237 that constitutes as the dish spring radially inner side axially on have a support 4241 that constitutes a hook-like part part, this support is connected with the inserting turning that the axial notch 4204a that is provided with in the dish spring is interconnected to constitute an axial interlocking.When wear sensor 4237 can avoid not existing wearing and tearing on friction pad 4207 abrasion detection ring 4220 is adjusted.Abrasion detection ring 4220 and wear compensation ring 4218 are concentric and be located on its radially inner side.

Wear compensation ring 4218 and abrasion detection ring 4220 have respectively at the upwardly extending and axial raised rising sloping platform 4219,4223 of circumference, and they are distributed on the periphery of ring 4218,4220.Encircling 4218,4220 is such installation in clutch 4201, promptly should pass through the rising sloping platform 4219,4223 of wedge shape or convex shaped moulding part formation towards shell bottom plate 4202a by ring.

Rising sloping platform 4219,4223 axially support are on opposed rising sloping platform 4221,4222, and in described embodiment, opposed rising sloping platform is formed directly on the shell 4202 by for example casting, promptly on the cover plate 4202a.

Rising sloping platform 4219 and 4223 and set opposed rising sloping platform 4221,4222 be to constitute so in a circumferential direction, promptly they can guarantee to encircle 4218,4220 at least one rotational angle that turns over respect to shell 4202 and can carry out at least a compensation to the wearing and tearing on the wear surface that appears at platen 4203, opposed platen 4206 and friction pad 4207 in during the whole operating life of friction clutch.Specially suitablely be, make the friction energy that when set rising sloping platform 4219 and 4221 or 4223 and 4222 compresses mutually, forms prevent to produce between the interactional rising sloping platform to slide, so in fact will form automatic brake if rising sloping platform 4219,4223 and opposed rising sloping platform 4221,4222 axial interactional lift angles are chosen as by friction.This lift angle can be 3 °-12 ° the order of magnitude.

On tangential, that is to say and adjusting on the direction, and cause owing to rising sloping platform 4219 and 4221 wear compensation ring 4218 towards the direction of platen 4203 with deviate from shell and radially make wear compensation ring 4218 be applied in elastic load on the direction of the axial generation axial displacement of section 4002a.In described embodiment, at least one helical spring 4228 that is located between two rings 4218,4220 that upwards can see from the footpath of the elastic load of wear compensation ring 4218 guarantees.Equally, abrasion detection ring 4220 is applied the circumferencial direction elastic load adjusting on the direction, that is to say, as shown in Figure 88 B, load by at least one helical spring 4229, this spring can be arranged on between the interactional ring 4218 of serial fashion and 4220 with compressing.Helical spring 4228 is upwards stretching and at the axial drift angle support plate 4241a of dish spring 4237 with encircle between the radial protrusion 4234 that forms on week in 4218 and compress in week.Abrasion detection ring 4220 has at least one radial protrusion 4235 on outer rim, this projection overlaps mutually with radial protrusion 4234.On projection 4234 and 4235 or in be provided with groove so as to keep and guiding at least a little by the helical spring 4229 of precharge.Because projection 4234 loads to projection 4235, so wear compensation ring 4218 is restricted with respect to relatively rotating of abrasion detection ring 4220.Two springs 4228 and 4229 join with the mode of action of series connection.As seeing, can encircle at each a spring 4228 is set on 4218,4220 at least from Figure 84. Ring 4218,4220 has Support 4234a, 4235a, and the Support is staggered on circumferentially.Dish spring 4237 have too be suitable for each spring 4228 single on circumferentially staggered Support or loading zone 4241a, 4241b.Wear sensor 4237 can prevent that abrasion detection ring 4220 from carrying out inappropriate adjustment when wearing and tearing do not take place, and from this on the one hand, also can avoid the improper adjustment of wear compensation ring 4218 conversely.If do not occur wearing and tearing on the friction pad 4207, projection 4234,4235 will be close to each other so.In order to ensure this state, in the time limit, helical spring 4228 should be greater than helical spring 4229 formed torque between two rings 4218,4220 at the moment of torsion that produces on the wear compensation ring 4218 in the whole operating life of friction clutch 4201.

The dish spring 4237 that plays the wear sensor effect is installed on the loading dish spring 4204, makes it have certain axial precompressed, i.e. precompression on the action direction of abrasion detection ring 4220.This can make the dish spring 4237 with this precompression lean against to load on the dish spring 4204 and be so to select to the reactive precompression of the adjustment of abrasion detection ring 4220, promptly when clutch is in closed and no state of wear and finish the wearing and tearing adjustment afterwards abrasion detection ring 4220 can not twist at clutch.The axial force that when friction clutch 4201 is in jointing state, under the axial force that produces on the abrasion detection ring 4220 must be greater than the situation with rising sloping platform 4222,422 3, forms by helical spring 4228 by diaphragm type wear sensor 4237.Must consider during wear sensor to act on perturbed force on the sensor, for example inertial force in design at the friction clutch duration of work.Also must avoid by wearing and tearing particularly pad wearing and tearing do not cause, make wear sensor 4237 mentioning from the abrasion detection ring 4220, because otherwise such danger can occur, promptly make abrasion detection ring 4220 produce and unwantedly reverse or adjust and thus wear sensor 4237 is compressed, thereby make the adjustment of friction clutch 4201 out of control.

To be axially disposed between platen 4203 and the operation dish spring 4204 at the secondary spring 4226 that works on the part area of friction clutch 4201 ventilation strokes at least.With compress and with the secondary spring 4226 that dish spring form constitutes be installed in the tapered direction of platen 4203 on so that keep dish spring 4226 to rotate with respect to operation dish spring 4204.Secondary spring 4226 can be finished and secondary spring 4026 identical functions shown in the secondary spring 4126 shown in Figure 87 and Figure 81, can consult above-mentioned relevant explanation to this.

Have the groove that axially is arranged in a linear on dish spring type wear sensor 4237, operation dish spring 4204 and the secondary spring 4226, at least one is fixed on the platen 4203 and axially extended pin 4203a can pass these grooves.Can make parts 4237,4204 not only face toward platen 4203 but also form antitorque commentaries on classics relative to one another by pin 4203a fixes.The radially inner side of the tongue 4204b of operation dish spring 4204 has the operation piece of tractive disk body 4260 forms, and this operation piece is by for example separation support generation axial displacement of separating mechanism.Tractive disk body 4260 axially remains in the radially inner side district of tongue 4204b and has regional 4260a, can load to the radially inner region of the tongue 4226a of auxiliary dish spring 4226 by this zone.

Annular loading zone 4260a is by the radial outside section constitution of disk body 4260.The tongue 4226a of secondary spring 4226 and and its coefficient loading zone 4260a between have axial distance 4232, this that is to say the effect that just is subjected to platen 4203 after friction plate 4207 discharges apart from guaranteeing to make auxiliary dish spring 4226 only in the ventilation stroke.

Shown in the new state of being described among Figure 88 A, when when clamping clutch disk 4208, being installed in friction clutch 4201 on the opposed platen 4206 radially inner side of dish spring 4204 will be turned right in clutch separation, so as to make the radial outside of dish spring 4204 be supported on by wear compensation ring 4218 with rotary support 4212.Be axially fixed between dish spring 4204 and the abrasion detection ring 4220 till the angle gap L between determined sensor spring 4237 of the projection of platen 4203 and the dish spring 4204 reaches at separation phase sensor dish spring 4237, dish spring 4204 is taken out to being bearing on the abrasion detection ring 4220.Dish spring 4204 centers on the ring-shaped bearing district 4220a revolution that forms on the abrasion detection ring 4220 duration of separating action, the roll extrusion support 4212 of 4204 pairs of radial outsides of dish spring is reduced pressure, so just can be when the generation wearing and tearing by encircling the 4218 suitable compensation of axial adjustment realization to wearing and tearing.Dish spring 4204 also can at first resemble between separation period the single-arm lever and rotate around outside roll extrusion support 4218.After surpassing slit or angle L, the annular rotational area of dish spring 4204 radially inwardly moves among the regional 4220a of abrasion detection ring 4220, thereby turns round or the generation effect as a double-arm lever at separating action duration chien shih dish spring 4204.During friction clutch 4201 is done, the power transmission that the moving of annular revolution (roll extrusion) supporting that effect by dish spring 4204 causes can be used in the power of determining that 4204 actions of dish spring are required than or lever ratio change from I to I-1, thereby, Separating force will occur and increase as long as dish spring 4204 supports on the abrasion detection ring 4220.Should be understood to than I for power transmission: I is the ratio of the distance of operation dish spring 4260 between the zone of projection 4213 loadings of the distance between the contact area of the pinch zones in the dish languid portion 4204 and dish spring 4204 and pivoting support 4212 and this contact area and 4204 pairs of platens 4203 of dish spring.Above-mentioned velocity ratio changes based on a kind of like this hypothesis, makes that promptly supporting and the supporting of dish spring 4204 on abrasion detection ring 4220 between dish spring 4204 and the platen 4203 forms approximately equalised diameter at least.Supporting area between dish spring 4204 and the abrasion detection ring 4220 is big more at rotary support 4212 radially outer direction top offsets, acts on more little that the Separating force of the dish spring arrangement on the abrasion detection ring 4220 improves.At one wherein among the embodiment of supporting diameter between dish spring 4204 and the abrasion detection ring 4220, formed the velocity ratio bigger than I-1 during around 4220 revolutions of abrasion detection ring than above-mentioned power transmission at dish spring 4204 greater than the supporting diameter between dish spring 4204 and the platen 4203.Yet the power transmission of being adjusted when friction clutch 4201 separates is than not comparing I greater than the power transmission of dish spring 4204.

As long as wearing and tearing occur on friction plate 4207 in the engaging process of clutch, the gradient of dish spring 4204 will change, and then the lip of the tongue 4204c will be moved to the left together with disk body.Because this changes in pitch can make abrasion detection ring 4220 load, so can adjust accordingly to the friction pad wearing and tearing that occurred.When wearing and tearing occurring, at first should be shown in Figure 88 B make abrasion detection ring 4220 relative wear compensated loops 4218 quick rotation formerly like that.Rotation by abrasion detection ring 4220 has formed between the supporting convex 4234,4235 of two rings 4218,4220 and the proportional gap 4245 of wearing and tearing.In the separation process of carrying out at present, as mentioned above, load to wear compensation ring 4218 by dish spring 4204, so that compensated loop can suitably be adjusted gap 4225.Make dish spring 4204 have one and corresponding gradient of new state or control position again thus.Along with the increase of wearing and tearing, dish spring 4204 produces in the axial direction and deviates from moving of cover plate 4202a direction, finishes the respective angles correction to dish spring 4204 mounting points simultaneously in whole adjustment district.This corresponding correction surveys according to abrasion detection ring 4220 respectively or detected abrasion condition carries out.

Relation between the characteristic curve that will provide according to Figure 89 is described in detail spring 4204,4226,4237 respectively now.

Curve 4261 among Figure 89 is illustrated in dish spring 4204 taperings and changes and considered under the situation of torque transmitter, for example the regional area of the formed distribution curve of axially making a concerted effort of power that is produced between shell and platen 4203 by plate spring member.This curve is to form when distortion appears in the dish spring between rotating support 4212 and projection 4,213 4204.Complete characteristic curve is the sinusoidal structure but has omitted the part that prolongs left at this.The complete distribution of curve 4261 looks to have and line 4033 similar shapes shown in Figure 84.Horizontal ordinate is represented the stroke to axial between two supportings or the support 4212,4213 and ordinate was represented by making a concerted effort that dish spring 4204 and torque transmitter produce.The mounting point of point 4262 representatives dish spring 4204 when clutch 4201 closures.The axial tensile force that curve 4263 expression pad springs 4210 produce between friction pad 4207.When friction clutch 4201 separates, spring sheet 4210 in stroke 4264 on decompression.In this stroke corresponding 4264, can promote the separation process of clutch by the pad spring 4210 that is provided with between the friction pad 4207 with the corresponding axial displacement of platen 4203.With dashed lines 4265 is illustrated in the stroke 4264 in Figure 89, the power distribution curve that makes clutch separation that produces on the zone of projection 4213.These power that in stroke 4264, form be equivalent to respectively dish spring 4204 power distribution curve 4261 and the pad spring 4210 power distribution curve 4263 between difference.The distribution curve of the clutch separation power that in fact forms in the zone of the lip of the tongue 4204c is compared with power distribution curve 4265 and has been reduced the magnitude of dish spring power transmission than I.When surpassing point 4268, on part is separated the end of stroke 4264, friction pad 4207 is discharged,, the Separating force that after this forms and point 4262 corresponding Separating forces are compared greatly reduced simultaneously along with the successively decreasing of dish spring 4204 characteristic curve districts.Under the situation that is provided with secondary spring 4226 effects, the Separating force of clutch 4201 will reduce till minimum point that reaches sinusoidally characteristic curve 4261 or valley point 4269 always.

The minimum value 4269 that dish spring 4204 is designed so that its characteristic curve 4261 in described embodiment is positioned under the axis of abscissa.When surpassing the point 4270 that is positioned on the axis of abscissa, 4261 corresponding positions will be sought to occupy voluntarily and be put to dish spring 4204, and constitute so-called snap structure for this reason, and this snap structure has unloading and loads two kinds of different state of equilibrium.

As from the part area of putting the line 4261 that dotted lines such as 4268,4269,4270 represent, seeing, under the situation that is not subjected to secondary spring 4226 effects, after friction plate pad 4207 discharges, because platen 4003 is axially mentioned, the variation of tangible power appears in the Separating force distribution curve.By using compensation spring 4226 can with the residue that release travel 4264 is joined separate make the Separating force distribution curve remain on lower in the stroke 4271 and relative constant level on.The power distribution curve that curve 4272 among Figure 89 forms in the zone of projection 4213 when turning round together corresponding to dish spring 4204 and dish spring 4226.Yet the Separating force distribution curve from the lip of the tongue 4204 to this section zone that dish spring 4204 is supported on the abrasion detection ring 4220 is compared the level of the velocity ratio I that reduced dish spring 4204 with the curve 4272 shown in Figure 89.In Figure 89 with the 4273 corresponding strokes of representing with platen 4203 of ventilation stroke.Secondary spring 4226 has the power shown in the line 4274-stroke characteristic curve.At least in remaining separation stroke 4271, dish spring 4204 and secondary spring 4226 have reverse power-flight distribution curve.In ventilation stroke 4273, power distribution curve 4272 is to form by characteristic curve 4261 that will exist in the ventilation stroke 4273 and 4274 curve addition.At this,, that is to say and bring into use distribution curve 4272 with joint efforts at the starting point place of ventilation stroke 4273 at point 4268 places.The structure of regional 4260a generation effect on secondary spring 4226 tongues of operation disk body 4260 also is to begin at point 4268 places of Figure 89.

As mentioned above, after finishing ventilation stroke 4273, dish spring 4204 forms axially mounting above abrasion detection ring 4220.Make the standard power transmission that is suitable for 4204 operations of dish spring than becoming I-1 thus from I.In Figure 89, represent the consequent Separating force that slightly raises with 4275.Hold the Separating force of this rising in the adjustment stroke 4267 relayings continuation of insurance of joining with the ventilation stroke.Be used for to friction pad 4207 carry out the required adjustment stroke 4276 of wear compensation and total to separate that stroke compares be very little and in a few tenths of millimeter or littler scope.

In order to keep being suitable for the tip of the tongue 4204c district or this necessary operations power, before point 4275 with existing velocity ratio I divided by the power shown in Figure 89 or power distribution curve and after putting 4275 with power transmission than I-1 divided by power among the figure or power distribution curve.In order to keep suitable operational stroke in the tip of the tongue 4204c district, after point 4275, multiply each other with the power transmission stroke more to that indicated in the drawings than I-1 multiplying each other with the stroke shown in Figure 89 than I with power transmission before the point 4275.Power transmission only is to establish for exceeding a little 4275 trip segment 4276 than I-1.

Use according to the designed friction clutch of the present invention and the loss that causes owing to tongue bends when the clutch separation can be reduced to minimum level, this be because friction clutch when being in separated state, to act on power on the lip of the tongue 4004c, 4104c and the 4204c very little even might be negative value shown in Figure 89.The latter means that the dish spring is inclined to the position of separation automatically in the negative value district of characteristic curve 4261.But this can compensate by secondary spring 4226.This in the operation dish languid portion compared much smaller load with conventional clutch can make the separate rows journey shorten, because as mentioned above, and the loss of travel that does not in fact exist the elastic bending owing to tongue and lid to cause.

In addition, according to the present invention the designed friction clutch of Figure 88 A can also be when clutch operating loss of travel during with shell or lid 4202 elastic return be reduced to minimum.Can realize like this, the elastic force of lid when making the axial elastic force that when friction clutch 4201 is closed, clutch lid 4202 is formed by dish spring 4204 equal clutch separation and dish spring 4204 to be supported on the abrasion detection ring 4220 by suitably designing friction clutch 4201, when friction clutch is closed, the axial force maximum that dish spring 4204 produces on lid 4202, but in the loading diameter of roll extrusion support 4212 and the free bend length minimum between the lid spiral fastening piece 4202b.When friction clutch separates, axial force that produce or that obtain from lid 4202 power of depressing of dish spring 4204 when closed less than friction clutch 4201 significantly by dish spring 4202 and secondary spring 4226.But the free lever length of lid 4202 or free spring length are obviously greater than the radial distance between rotary support 4212 and its screw-thread securing piece 4202b between the supporting diameter 4220a of abrasion detection ring 4220 and the threaded fasteners 4202b.

Friction clutch 4301 shown in Figure 90 has from the structure of the dish spring 4337 that uses as wear sensor structure and the working method identical with the clutch 4201 shown in Figure 88 A.Operation dish spring 4304, wear sensor spring 4337 possess identical functions with the described relevant parts 4204,4226 and 4237 of secondary spring 4326 and the plotted curve of Figure 88 A and Figure 89.Wear compensation ring 4318 and abrasion detection ring 4320 with Figure 88 A in ring 4218 and 4220 same modes by rising sloping platform and opposed rising sloping platform and set shell 4302 interactions.

Dish spring 4326 is by elastic component 4344 prestressing between eseparation ring 4360 and dish spring 4304, so that can carry out axially locating equally when clutch.

Sensor dish spring 4337 has the structure of another kind as the sensor dish spring 4237 of Figure 88 on the prestressing position shown in Figure 90.The radially inner side of this dish spring 4337 is supported on the operation dish spring 4304 and the residing annular region of its continuous radial outside applies towards the load of shell 4302 directions to wear ring 3320.Spring 4337 has radially support 4342, can make spring face toward adjustment by this support and encircle 4318 supporting 4343 placements and keep precompressed on air course L when clutch is closed.Have the tongue 4341a that axially faces toward shell 4302 on the radial outside of sensor 4337, this tongue is used for supporting effect in the adjustment spring 4328 that makes progress in week.

The clutch device that has friction clutch 4401 shown in Figure 91 except that the mounting point of auxiliary dish spring 4426 and the slightly different working method, has the structure identical with the clutch device shown in Figure 87.

In order to adapt to some application, according to required clutch characteristics of clutch 4401 and the installing space that is possessed, concerning main dish spring 4404 its relevant stroke-force characteristic curve, especially in required separation stroke (curves 4046 among Figure 84), design is not best.Can in separation process, will be exceeded greater than the point of adjusting on the last later dish spring characteristic curve (4033 among Figure 84) of the axially support power to dish spring 4404 that exists of point (4037 among Figure 84) (4039a among Figure 84) like this at Separating force.This also means, in fact point 4039 is arranged on the point 4045 of Figure 84 or on the further along position, that is to say at the end points place of required separation stroke or surpasses on the stroke very short after separating stroke.This surmounting may cause, and in unallowable big stroke, exchanges the domain 4417 by dish spring 4404 and carries out axial decompression and make to adjust to encircle adjusting accordingly.Also may when there are not wearing and tearing in clutch friction pad 4407, it not adjusted thus.This also can make the mounting point, operation point of dish spring 4404 change when friction clutch is in jointing state, that is to say precompression or pressure are changed to the direction that diminishes.This means, in this clutch device, in the curve shown in Figure 84 with 4037 operation points of representing along with 4033 displacements of the corresponding characteristic curve of the direction that surmounts minimum value 4038a or move.The moment that therefore possible corresponding minimizing is transmitted by friction clutch, thus cause clutch to break down.

This undesirable adjustment of carrying out for fear of regulating mechanism 4416, dish spring 4426 is arranged between adjustment ring 4417 and the dish spring 4404 like this, promptly when surpassing unallowed maximum separation stroke at least, this dish spring 4426 should be as blocking device or break to controlling device generation effect.Therefore can also exceed the normal separation stroke more for a long time and/or when axial members is swung, avoid friction clutch 4401 is carried out unsuitable adjustment.

The secondary spring 4426 that constitutes with dish spring form is to be provided with like this adjusting between ring 4417 and the dish spring 4404, promptly begin this secondary spring tensioning, make dish spring 4436 prop up operation dish spring 4404 and load to adjusting ring 4417 from a definite separation stroke of adjusting between ring 4417 and the dish spring 4404.In fact the zone of adjusting ring 4417 is held or clamps between two dish springs 4426 and 4404.Therefore can exchange the domain 4417 since a definite separation stroke provides and reverses protection.

Secondary spring 4426 has annular matrix 4427, has radially support 4428 on the periphery of matrix, and as from seeing Figure 92 and 93, support is along the tangential distribution of matrix 4427 and be overlapped among the radial groove 4417a that adjusts ring 4417.Auxiliary dish spring 4426 has braking edge 4422, and the braking edge is to be made of the radially tongue 4422 that forms on week in matrix 4427.These braking edge 4422 interact with the moving edge 4430 of counter that is located on the dish spring 4404.In described embodiment, the moving edge 4430 of counter is that the termination by riveting parts 4431 constitutes, and riveting parts 4431 is arranged in the zone of tongue 4404b of dish spring 4404.Also can use and auxiliary dish spring 4426 all-in-one-piece tongues without riveting parts 4431, this tongue is with the mode and braking edge interaction similar to tongue 4122 and corresponding dish spring 4104 among Figure 87.

Be under the closed state at friction clutch, the distance 4432 between the moving edge 4430 of braking edge 4422 and counter is to arrange like this, promptly can not come in contact between braking edge 4422 on the partial journey of clutch release travel and the moving edge 4430 of counter at least.Braking edge 4422 is touched on the moving edge 4430 of counter.When determining the separation stroke in stage above these, auxiliary dish spring 4426 will the tensioning by means of main dish spring 4404, so as mentioned above, adjust ring 4417 and clamp and prevented because of reversing that peripheral force that helical spring 4420 produces causes making with respect to main dish spring 4404.

For the ease of installing and will assisting dish spring 4426 to install to rotationally and adjust on the ring 4417, encircle 4417 radially inner edge and be provided with a groove 4417a about its middle part that extends axially the district greatly in adjustment.

Shown in Figure 92 and 93, groove 4417a be form on the periphery of adjusting ring and also facing to dish spring 4404 axially on be provided with locating aperture or interruption.Therefore, adjust ring 4417 radial recess 4440 with axial distribution, this recess is in the state that is connected with the groove 4417a of tangential distribution.Constituting radially-protruding protruding 4441 on the adjustment ring 4417 between the recess 4440 that forms on the interior week of adjusting ring 4417.Recess 4440 on periphery distribution and quantity corresponding to the separation and the quantity of the support 4428 of auxiliary dish spring 4426.The extension that extend to the support 4428 that less be equivalent to correspondingly of recess 4440 on tangentially.Auxiliary dish spring 4426 and the assembling of adjusting between the ring 4417 can be by axially inserting support 4428 in the recesses 4440 and after this realizing by making to produce between two parts 4417 and 4426 to reverse relatively.Producing between above-mentioned two parts 4417 and 4426 on the basis of reversing relatively, shown in Figure 92, support 4428 and protuberance or projection 4441 are overlapped at least in the axial direction.On this overlapping basis, the moving edge 4430 of braking edge 4422 and counter form cooperate after, tongue or support 4428 can compress with respect to protuberance or protruding 4441 radially.

Auxiliary dish spring 4426 is such formations, and be to install like this in friction clutch 4401, promptly at separation phase, at least between a braking edge 4422 and the moving edge 4430 of counter, form in the separation stroke that cooperates, make that adjusting ring 4417 can not take place to reverse relatively with respect to auxiliary dish spring 4426.Preferably in separation process, occur afterwards above point of release (point 4037 among Figure 84) braking edge 4422 and breaking through the cooperation of moving between the edge 4430 just.Can guarantee like this to form friction pad 4407 is carried out reversing of the required adjustment ring 4417 of wear compensation.Be preferably in to make when auxiliary dish spring 4427 is in the actual state that compresses and adjust ring 4417 and produce reversing relatively with respect to auxiliary dish spring 4426.Shown in Figure 92, along with the increase of friction plate 4407 wearing and tearing, the projection 4441 of adjusting ring 4417 moves right with respect to tongue 4428.The peripheral length of projection 4441 and tongue 4428 is to determine like this, and it is overlapping promptly on the worn area of all permissions projection 4441 and 4428 to be formed on the clutch unit is axial at least.Be at friction clutch 4401 that auxiliary dish spring 4426 also can be compacted under the state of joint.Can realize like this, when before the joint stroke will finish, engaging, the tongue 4404b of main dish spring be cooperated with each tongue 4422a formation of auxiliary dish spring 4426, thereby auxiliary dish spring 4426 is compressed slightly towards the clutch lid to the right.Pressure maximum in the time of can also being in jointing state by 4426 pairs of clutches of dish spring thus limits.The height of pressure limit depends on that the characteristic curve of main dish spring 4404 and auxiliary dish spring 4426 distributes.

With regard to exchanging the adjection that the domain 4417 brakes, auxiliary dish spring 4426 has been brought into play and the identical effect of auxiliary dish spring 4126 among Figure 87.This dish spring equally also can cause making in the minimum value zone of dish spring 4404 at least the Separating force distribution curve to raise, and guarantees to make Separating force can keep constant distribution thus in separating stroke.Can consult explanation to Figure 81-90 to this.

The present invention is not restricted to the described embodiments, but generally is applicable to various friction clutches, and particularly those have the friction clutch of the mechanism that the wearing and tearing to friction pad compensate.In addition, the present invention also comprises some modification structures, and these modification structures can be by respectively with the described feature of different embodiments or parts are combined constitutes.Also can respectively the feature shown in the accompanying drawing or the mode of action be taken out independently invention of formation separately.The applicant keeps further requirement to the present right that the related feature of disclosed essence implication of the present invention is protected in specification.

Claims (188)

1, a kind of friction clutch that is particularly suitable for Motor Vehicle, has a platen, this platen is not rotating but can do axially that limited mobile mode links to each other with shell, a dish spring that produces extruding force is axially compacted between shell and platen simultaneously, this dish spring is on the one hand around the pivoting support revolution that is bearing on the shell, on the other hand platen is pressed to a direction between platen and the opposed platen as the clutch disk that clamps of flying wheel, one of them can compensate and be carried continuously by an advancing means the wearing and tearing of the friction pad of clutch disk at least, and act on that the pivoting support that is being supported by shell in the automatic control tegulatingdevice can move in the axial direction between housing and the dish spring, and the dish spring is in the direction towards pivoting support under the effect of support force.

2, friction clutch according to claim 1 is characterized in that, the dish spring constitutes the characteristic curve that successively decreases in its working area.

3, friction clutch according to claim 1 and 2 is characterized in that, the dish spring only is to be supported by the power transfer mode opposite with Separating force.

4, according to the described friction clutch of one of claim 1-3, it is characterized in that, supporting force and disc spring force are to mate so each other, promptly on the mounting point of dish spring regulation with separating in the stroke when tapering not occurring and change at the dish spring because of wearing and tearing, supporting force is greater than the reaction force to supporting force that is produced by the dish spring, having under the situation of wearing and tearing when the tapering of dish spring changes, separating supporting force in the part area of stroke less than the power opposite that produces by the dish spring with supporting force at the dish spring.

According to the described friction clutch of one of claim 1-4, it is characterized in that 5, supporting force is by a power storage at least, for example spring forms, the adjustment period that abrasion condition is carried out between this supporting force can change the configuration of the supporting of dish spring or case side.

According to the described friction clutch of one of claim 1-5, it is characterized in that 6, controlling device is axially disposed between dish spring and the lid.

According to the described friction clutch of one of claim 1-6, it is characterized in that 7, controlling device has the elevation surface as sloping platform.

According to the described friction clutch of one of claim 1-7, it is characterized in that 8, supporting force is formed by dish spring type parts.

9, according to the described friction clutch of above-mentioned at least one claim, it is characterized in that, be supported on the dish spring at the dish spring that produces supporting force on the radial height of axially movable supporting.

According to the described friction clutch of one of claim 1-9, it is characterized in that 10, the dish stage clip is bearing between two supportings of shell side pivotally, wherein prop up and afford the elastic load that pressing plate is applied towards the direction of dish stage clip.

11, friction clutch according to claim 10 is characterized in that, can move axially by the spring-loading supporting of supporting force.

According to the described friction clutch of one of claim 1-11, it is characterized in that 12, spring-loading supporting produces and the Separating force of dish stage clip reduced when mobile.

According to the described friction clutch of one of claim 1-12, it is characterized in that 13, spring-loading supporting moves to the dish stage clip till Separating force that produces in the supporting and the reaction force that is supporting formation reach equilibrium of forces always.

According to the described friction clutch of one of claim 1-13, it is characterized in that 14, load the reaction force that forms in the supporting in elasticity and produce by the power storage, this power storage has the power of substantial constant in the regulatory region that sets.

According to the described friction clutch of one of claim 1-14, it is characterized in that 15, the power storage that produces supporting force plays sensor.

According to the described friction clutch of one of claim 1-15, it is characterized in that 16, load in elasticity on the movement direction of supporting, reverse supporting set on the dish stage clip can move axially to the direction of platen, but brakes on opposite direction.

It is characterized in that according to the described friction clutch of one of claim 1-16 that 17, the advancing means that controlling device is carried continuously is a spring.

According to the described friction clutch of one of claim 1-17, it is characterized in that 18, controlling device has a relevant with it ring part, this ring part is subjected to the axial loading of dish stage clip when friction clutch is in jointing state.

According to the described friction clutch of one of claim 1-18, it is characterized in that 19, controlling device has the adjusting sloping platform of axial rising.

20, friction clutch according to claim 19 is characterized in that, regulates sloping platform and is arranged on the ring part.

21, according to the described friction clutch of one of claim 18-20, it is characterized in that, have an oppositely supporting on the ring part.

According to the described friction clutch of one of claim 19-21, it is characterized in that 22, rising sloping platform and corresponding opposed rising sloping platform interact.

23, friction clutch according to claim 22 is characterized in that, has opposed rising sloping platform on the ring part, and ring part is arranged between the parts and housing that have the rising ramp platform.

24, friction clutch according to claim 23 is characterized in that, opposed rising sloping platform is formed directly in the radially extension area of shell.

25, according to the described friction clutch of claim 1-24, it is characterized in that, but controlling device unrestricted motion on the detaching direction of friction clutch, and on the direction opposite with detaching direction automatic brake.

According to the described friction clutch of one of claim 19-25, it is characterized in that 26, the sloping platform that rises at least has a lift angle, this lift angle is 4 °-20 °, is preferably in 5 °-12 ° magnitude.

According to the described friction clutch of one of claim 19-26, it is characterized in that 27, the rising sloping platform has a lift angle, this lift angle carries out friction engagement by the opposed rising area of rising sloping platform and another parts and produces automatic brake.

28, according to the described friction clutch of one of claim 19-27, it is characterized in that, apply elastic load adjusting on the direction at least to parts that have the rising sloping platform and/or the parts that have opposed rising sloping platform or an opposed rising area.

According to the described friction clutch of one of claim 1-28, it is characterized in that 29, controlling device has a plurality of parts of movably regulating.

According to the described friction clutch of one of claim 10-29, it is characterized in that 30, controlling device is revolution type (Figure 12,13).

According to the described friction clutch of one of claim 1-30, it is characterized in that 31, controlling device is braked (Figure 12,13) according to revolution.

32, according to the described friction clutch of one of claim 1-31, it is characterized in that, when revolution surpasses certain boundary, make the controlling device locking.

33, according to the described friction clutch of one of claim 1-32, it is characterized in that, under idling speed or revolution controlling device is worked when being lower than idling speed.

According to the described friction clutch of one of claim 1-33, it is characterized in that 34, in fact controlling device begins to work when revolution is zero.

According to the described friction clutch of one of claim 1-34, it is characterized in that 35, having rising sloping platform and/or opposed rising sloping platform or opposed angled section and can be subjected to elasticity with respect to the part that shell moves on the controlling device loads.

36, friction clutch according to claim 35 is characterized in that, elastic load is generation power on tangentially.

According to the described friction clutch of one of claim 1-36, it is characterized in that 37, the radial outside area supporting of the sensor spring of generation reaction force is on shell.

38, according to the described friction clutch of one of claim 1-37, it is characterized in that, on shell, be provided with a supporting area that is suitable for forming the sensor spring of reaction force.

According to the described friction clutch of one of claim 1-38, it is characterized in that 39, pad spring or pad spring substitute material are arranged between the friction pad of clutch disk.

40, according to the described friction clutch of one of claim 1-39 particularly, it is characterized in that, the pad spring that is provided with between the friction pad of clutch disk has a stroke-force characteristic curve, the stroke-force characteristic curve similar (Figure 18) of the power that this curve produces on pressing plate to the dish stage clip in the springing stroke of pad spring.

According to the described friction clutch of one of claim 1-40, it is characterized in that 41, when friction clutch was in separated state, making dish stage clip or the needed power of friction clutch work was-150 to 150Nm magnitudes.

42, according to the described friction clutch of one of claim 1-41, it is characterized in that, after clutch disk discharges, make the dish spring transfer negative power-flight distribution curve (Figure 18) to from positive power-flight distribution curve by opposed platen.

43, one of require the described friction clutch that is particularly useful for Motor Vehicle according to aforesaid right particularly, has a platen, this platen can not rotate but can do and axially limitedly link to each other with shell movably, between shell and platen, be provided with simultaneously an operating device and a force-storing device at least, can apply towards in a load between itself and the opposed platen to platen by them as the clutch disk direction that clamps of flywheel, wherein has the controlling device that an energy compensates the friction pad occurring wear of clutch disk at least, this controlling device comprises a wear compensation device that is arranged between operating device or force-storing device and the platen, compensation device between operating device or force-storing device and platen carries out corresponding axial adjustment to the wearing clearance of friction pad, after the corresponding adjusting that the actual wear state of friction pad is done is finished, wear compensation device is limited on its regulatory function by the mechanism that is located on the platen.

44, according to the described friction clutch of one of claim 1-43, it is characterized in that, the dish spring of an axial compression is set between shell and platen, this dish spring can turn round around a ring-shaped bearing of shell support and have an annular matrix that is used to form force-storing device, and the tongue that extends radially inwardly stretches out from this annular matrix.

45, according to the described friction clutch of one of claim 1-44, it is characterized in that, the limting mechanism of compensation device is made of a wear sensor at least, this wear sensor has a sensing element that oppositely moves with platen, and this sensing element is by being provided with the separation stroke that the axial restraint parts limit platen.

46, according to the described friction clutch of claim 45, it is characterized in that, sensor element can move axially and by automatic regulating apparatus and axially movable parts for example platen link to each other, but also can be by at least one Axial Mounting Part such as shell being set and/or opposed platen is adjusted it.

According to claim 45 or 46 described friction clutches, it is characterized in that 47, movably sensor element has a contact area, this contact area interacts when friction clutch separates with the opposed contact area of the compensating unit of compensation device.

48, according to the described friction clutch of one of claim 45-47, it is characterized in that movably sensor element is bearing on the platen by controlling device.

49, according to the described friction clutch of one of claim 1-48, it is characterized in that, compensation device comprises a support unit that is used for force-storing device, and between this support unit and platen, being provided with a compensation device, this compensation device weares and teares automatically to support unit when friction clutch separates and adjusts and Braking mode during in clutch.

According to the described friction clutch of claim 49, it is characterized in that 50, supporting can move axially leaving on the direction of pressing plate, towards pressing plate axially on then produce braking.

According to the described friction clutch of claim 1-50, it is characterized in that 51, compensation device has the effect that can move freely when friction clutch separates, and when friction clutch engages automatic brake.

According to the described friction clutch of one of claim 1-49, it is characterized in that 52, compensation device has a compensating part that is made of ring part.

According to the described friction clutch of claim 52, it is characterized in that 53, ring part is supported on the platen opposite by sloping platform.

According to the described friction clutch of claim 53, it is characterized in that 54, sloping platform and opposed sloping platform interact.

According to the described friction clutch of claim 54, it is characterized in that 55, sloping platform and opposed sloping platform compress mutually by spring.

According to the described friction clutch of one of claim 52-55, it is characterized in that 56, annular element forms the sheet component with hole, U-shaped cross section, in the free space of parts, be equipped with and be distributed in wedge-shaped member on the periphery and that constitute by sloping platform.

According to the described friction clutch of claim 56, it is characterized in that 57, wedge-shaped member is lockable with respect to annular element and does not rotate.

According to claim 56 or 57 described friction clutches, it is characterized in that 58, wedge-shaped member can produce with respect to annular element and move axially.

According to the described friction clutch of claim 54-58, it is characterized in that 59, opposed sloping platform is made of wedge, this wedge to small part snap in by annular compensating part around free space in and can rotate with respect to platen and compensating part.

According to the described friction clutch of claim 47-59, it is characterized in that 60, compensating part is lockable with respect to platen and does not rotate.

According to the described friction clutch of one of claim 53-60, it is characterized in that 61, opposed sloping platform is flexibly loaded towards the sloping platform direction.

According to the described friction clutch of claim 61, it is characterized in that 62, elastic load is that for example helical spring forms by the spring of pressurized between the parts that constitute sloping platform and opposed sloping platform.

63, according to the described friction clutch of one of claim 53-62, it is characterized in that, constitute parts section axial clamping at least between parts that constitute sloping platform and compensating unit of opposed sloping platform.

According to the described friction clutch of one of claim 53-63, it is characterized in that 64, the petiolarea at the spring that sloping platform and opposed sloping platform are compressed should lead by the parts that constitute sloping platform and opposed sloping platform at least.

According to the described friction clutch of one of claim 53-64, it is characterized in that 65, the parts that constitute sloping platform and/or opposed sloping platform are made of heat insulation and heat-resistant material.

According to the described friction clutch of one of claim 53-65, it is characterized in that 66, the parts that form sloping platform and/or opposed sloping platform are by heat-resistant material, for example thermoplastic or thermosetting plastics constitute.

According to the described friction clutch of one of claim 53-66, it is characterized in that 67, the material that constitutes sloping platform parts and/or opposed sloping platform parts has high coefficient of friction.

According to the described friction clutch of one of claim 1-66, it is characterized in that 68, during clutch separation, the stroke of dish spring is greater than the part of leaving of the platen that is limited by limting mechanism in the platen that is subjected to the effect of dish spring loads the diameter region scope.

According to the described friction clutch of claim 68, it is characterized in that 69, compensation device all unloads in each separation process.

70, according to the described friction clutch of claim 1-69, it is characterized in that, compensation device has two sloping platform members that are adjacent to mutually, wherein, sloping platform member can not rotate and another sloping platform member can not be with respect to can being reversed by the compensating part that force-storing device loads with respect to platen, but compensating part can rotate with respect to platen.

71, a kind of friction clutch that is specially adapted to Motor Vehicle, has a platen, this platen can not rotate but can do and axially limitedly link to each other with shell movably, while dish-shaped stage clip axial compression between shell and platen, this dish spring can rotate around an annular pivoting support that supported by shell on the one hand, apply towards one between platen and the opposed platen as the clamped clutch disk direction ground of flywheel load to platen on the other hand, but also has a controlling device that the friction pad occurring wear on the clutch disk is compensated, it is characterized in that, between pressure dish spring and platen, be provided with a wear compensation device, this compensation device has one at least can axially movable compensating unit, the dish stage clip loads to compensating unit, in addition, the axial separation stroke of platen is limited and keep approximately constant at least by the limting mechanism that between platen and at least one Axial Mounting Part, forms, and at least when friction clutch separates, limting mechanism limits with respect to moving axially of platen compensating unit.

72, particularly according to one of the aforesaid right requirement described friction clutch that is particularly suitable for Motor Vehicle, has a platen, this platen not rotating but the mode that can make axial finite displacement link to each other with shell, a stage clip is set between shell and platen simultaneously at least, this stage clip can to platen apply towards between platen and opposed platen with a load as the clamped clutch disk direction of flywheel, and has a controlling device that an energy compensates the friction pad occurring wear of clutch disk, this controlling device produces the power load of a substantial constant to platen by stage clip, friction clutch also has and is used to engage and the operating device that separates and a damping device, in separation process, this damping device makes the moment by friction clutch or clutch disk transmission descend gradually on the part area of operating device operational stroke.

73, according to the described friction clutch of one of claim 1-72, it is characterized in that, friction clutch has a damping device, in separating stroke, this damping device produces on the partial distance that moves axially stroke in the platen district that loaded by stage clip the moment of friction clutch transmission is descended gradually.

According to claim 72 or 73 described friction clutches, it is characterized in that 74, this damping device is arranged in the power bang path between the fixed area of the shell on operating device or stage clip and the opposed platen.

According to the described friction clutch of one of claim 1-74, it is characterized in that 75, this damping device is arranged in the power bang path between the rubbing surface of operating device or stage clip and platen.

76, according to one of aforesaid right requirement described friction clutch, it is characterized in that this damping device is axially disposed between the friction pad of clutch disk.

77, according to the described friction clutch of one of claim 1-76, it is characterized in that, this damping device can produce axial elasticity between clutch component flexible, therefore damping device can be set like this, promptly when clutch is opened, make the power that acts on the damping device for minimum, and when clutch is closed, make the power that acts on the damping device increase to maximum gradually, and this increase should occur on the part area that engages stroke at least.

According to the described friction clutch of one of claim 1-77, it is characterized in that 78, damping device causes being reduced gradually at least or increase gradually by the moment of friction clutch transmission on about 40-70% operational stroke of operating device.

According to the described friction clutch of one of claim 1-78, it is characterized in that 79, stage clip has the power-flight distribution curve that successively decreases at least on the part area of friction clutch separation stroke.

80, according to one of aforesaid right requirement described friction clutch, it is characterized in that stage clip is made of the dish spring, this dish spring can wind the annular pivoting support that is supported by shell on the one hand and rotate, and loads to platen on the other hand.

81,0 described friction clutch according to Claim 8 is characterized in that the dish spring has annular solid, and the tongue of a formation operating device radially inwardly stretches out from annular solid.

82,0 or 81 described friction clutches according to Claim 8 is characterized in that the dish spring between two supportings is bearing on the shell pivotally.

83, according to the described friction clutch of one of claim 79-82, it is characterized in that, the dish spring has sinusoidally power-stroke characteristic curve, and be at friction clutch under the state of joint, the drive point of dish spring is in since the decline characteristic curve district that the first maximum, force value forms, and the maximum, force value of this dish spring and the force rate between the minimum force value that forms thereafter are 1: 0.4-1: 0.7.

84, be provided with particularly at least Motor Vehicle according to one of aforesaid right requirement described friction clutch, clutch can be operated by the piece-rate system that acts on the operating device, wherein piece-rate system has clutch pedal, and the structure of this pedal is similar to gas pedal.

85, a kind of preassembled clutch pack, has pressing plate, this platen is not rotating but can make limited axially movable mode and link to each other with opposed platen, wherein at least one stage clip that is bearing on the shell applies load towards the clutch disk direction that can clamp to platen between platen and opposed platen, the controlling device that also has an abrasion that occurs at least can friction pad to compensate in addition to clutch, this controlling device produces the power load of substantial constant to platen by stage clip, this clutch pack has and is used to engage and the operating device that separates, and has a damping device, this damping device has an elastic component that in series is provided with stage clip at least, in separation process, damping device causes being reduced gradually by the moment of clutch disk transmission on the part area of operating device operational stroke.

86, a kind of clutch pack, has platen, this platen can not rotate but can do and limitedly link to each other with opposed platen with axial motion, wherein at least one stage clip applies load towards the clutch disk direction that can clamp to platen between platen and opposed platen, has a controlling device that can compensate occurring wear on the friction pad of clutch disk at least in addition, this controlling device applies substantially invariable power load by stage clip to platen, and this friction clutch also has and is used to engage and the control mechanism that separates and a damping device, in separation process, damping device causes being reduced gradually by the moment of friction clutch or clutch disk transmission on the part area of operating device operational stroke, in addition, opposed platen is mass block parts in the double quality blocks flywheel, its quality can overcome the influence of rotating the oscillation damping spring and produce relative rotation each other, and wherein another mass block parts link to each other with the live axle of internal-combustion engine.

87,6 described clutch packs according to Claim 8 is characterized in that, shell and the flywheel loaded components that is made of opposed platen form being rotationally connected that non-destruction can not free.

88,6 or 87 described clutch packs according to Claim 8 is characterized in that damper is arranged on the radial outside of clutch disk external diameter.

89, a kind of and internal-combustion engine uses together, the clutch pack that is particularly useful for Motor Vehicle, it comprises a friction clutch that has platen, platen is not rotating but can make limited axially movable mode and link to each other with opposed platen, have at least one stage clip in addition, this stage clip applies the load of clamped a clutch disk direction as flywheel between platen and opposed platen to platen; Friction clutch has a controlling device that can compensate occurring wear on the friction pad of clutch disk, this controlling device is producing substantially invariable power load by stage clip during the operating life on platen, also have and be used to engage and the operating device that separates, comprise a damping device in addition, this damping device makes on the part area of operating device operational stroke the moment by friction clutch or clutch disk transmission reduce gradually in separation process, wherein friction clutch is connected with the live axle of internal-combustion engine by an axial elasticity spare, the intensity of elastic component is to set like this, the axial vibration that promptly utilizes elastic component on clutch, to produce by live axle, swing is vibrated or flexure vibrations reduce or be suppressed to certain ratio, so just can guarantee friction clutch, especially its controlling device plays one's part to the full.

90,9 described clutch packs according to Claim 8 is characterized in that, the intensity of parts is to set like this, promptly props up the required steering force of clutch separation by parts clutch pack is not moved axially basically.

91,9 or 90 described clutch packs according to Claim 8 is characterized in that damping device has an elastic mechanism, the setting that is connected with stage clip of this elastic mechanism.

92, the described clutch pack of 9-91 according to Claim 8 is characterized in that opposed platen links to each other with the live axle of internal-combustion engine by damper.

93, a kind of transmission device that is specially adapted to Motor Vehicle, being located at the operation according to reduction gear between drive motor and the reduction gear by automatic or automanual reduction gear and one controls the controlled friction clutch of (or adjusting) and constitutes, this friction clutch dish has a platen, platen is rotatable but can do axially limitedly to connect together with an opposed platen that can link to each other with the live axle of drive motor movably, also comprise at least one stage clip, this stage clip applies towards the load of one between platen and opposed platen the clamped clutch disk direction as flywheel to platen, has a controlling device that can compensate occurring wear on the friction pad of clutch disk at least simultaneously, this controlling device can produce substantially invariable power load to platen by stage clip, have in addition and be used to make friction clutch to engage and the operating device that separates and a damping device, this damping device makes the moment of friction clutch or clutch disk transmission reduce gradually in separation process on the part area of operating device operational stroke.

According to the described transmission device of claim 93, it is characterized in that 94, stage clip forms the power-stroke characteristic distribution curve that successively decreases at least on the part area of separating stroke.

According to claim 93 or 94 described transmission devices, it is characterized in that 95, damping device reduces the moment of friction clutch transmission gradually or increase to be gradually to work on the 40-70% that is approximately operating device and/or platen operational stroke.

96, particularly according to one of aforesaid right requirement described clutch pack, has a platen, this platen can not rotate but can do and axially limitedly link to each other with an opposed platen movably, wherein at least one stage clip applies load towards the clamped clutch disk direction between platen and opposed platen to platen, in addition, also has a controlling device that can compensate occurring wear on the friction pad of clutch disk at least, this controlling device applies substantially invariable power load by stage clip to plate, friction clutch has and is used to the operating device that separates and engage, this operating device can be operated by the axially movable separator of separating mechanism by means of one, simultaneously operating device should in separating stroke, produce according to the wear extent of abrasion pad at least move axially and also the power bang path between separating mechanism and operating device in an energy is set moving axially of operating device is carried out the damping device of approximate equilibrium at least.

97, according to the described clutch pack of one of claim 1-96, it is characterized in that, balance and buffer device is located between separator and the operating device.

98, according to the described clutch pack of claim 1-97, it is characterized in that, friction clutch has a shell that can be fixed on the opposed platen, steel plate lid for example, have a base plate that separator is moved on the shell, and balance and buffer device can be between operating device and base plate axial compression.

99, according to the described clutch pack of one of claim 1-98, it is characterized in that, but stage clip is the dish spring by axial compression between clutch outer member and platen to be constituted, and this dish spring has a flexible annular matrix and the tongue of the formation operating device that extends radially inwardly from matrix.

According to the described clutch pack of one of claim 1-99, it is characterized in that 100, balance and buffer device has the adjustment sloping platform of rising in the axial direction.

101, according to the described clutch pack of one of claim 1-100, it is characterized in that, adjust sloping platform and constitute by the rising sloping platform that on ring part, is provided with at least.

According to claim 100 or 101 described clutch packs, it is characterized in that 102, adjust sloping platform and comprise opposed rising sloping platform, this opposed rising sloping platform and rising sloping platform interact.

According to the described clutch pack of one of claim 1-102, it is characterized in that 103, opposed rising sloping platform is located on the ring part equally.

104, according to the described clutch pack of one of claim 100-103, it is characterized in that, have the parts of adjusting sloping platform and can produce mobile in the axial direction.

According to the described clutch pack of one of claim 101-104, it is characterized in that 105, the parts that have rising sloping platform and opposed rising sloping platform can reverse each other relatively.

According to the described clutch pack of one of claim 101-105, it is characterized in that 106, one of parts with sloping platform or opposed rising sloping platform can not rotate relative to friction clutch.

According to the described clutch pack of one of claim 100-106, it is characterized in that 107,, adjust sloping platform and have lift angle that this lift angle can form automatic brake by the friction engagement of adjusting sloping platform.

According to the described clutch pack of one of claim 100-107, it is characterized in that 108, adjusting the lift angle that sloping platform has is between 4 ° to 20 °, preferably 5 °-12 ° magnitude.

109, according to the described device assembly that closes of one of claim 101-108, it is characterized in that, at least one have parts modulated perfect square that rising sloping platform and/or one has an opposed rising sloping platform to the elastic load effect.

110, according to the described clutch pack of one of claim 101-109, it is characterized in that, the parts that have the parts of rising sloping platform and/or have an opposed rising sloping platform are subjected at least one and are arranged on force-storing device between two parts, and for example helical spring is being adjusted load or the impacting force that applies on the direction.

According to the described clutch pack of one of claim 1-110, it is characterized in that 111, it is in order to limit separating stroke that damping device is set.

According to the described clutch pack of claim 111, it is characterized in that 112, damping device has a bounding means at least.

According to claim 111 or 112 described clutch packs, it is characterized in that 113, limit stoper forms between separator and clutch lid.

According to the described clutch pack of one of claim 111-113, it is characterized in that 114, separator has a clutch separation supporting and bounding means can be movable between supporting ring that rotates with friction clutch and clutch lid.

According to the described clutch pack of one of claim 111-114, it is characterized in that 115, limit stoper is arranged between the separator conduit of establishing on the back flow side and separator.

116, according to the described clutch pack of one of claim 1-115, it is characterized in that, be provided with mechanism, this mechanism makes the moment of friction clutch or clutch disk transmission reduce gradually in separation process on the part area of operating device operational stroke.

117, according to the described clutch pack of one of claim 1-116, it is characterized in that, the stage clip that is made of the dish spring is bearing between two supportings on the clutch outer member pivotally, be subjected to platen by two supporting stage clips and move the elastic load that applies to the direction of stage clip, wherein when friction clutch separates, the dish spring can increase when friction pad weares and teares and surpass in the power that produces in the spring-loading supporting and acts on elasticity and load power in the supporting.

According to the described clutch pack of claim 117, it is characterized in that 118, spring-loading supporting can move axially.

According to the described clutch pack in one of claim 117 or 118, it is characterized in that 119, when the Separating force of dish stage clip increased, elasticity loaded supporting and moves to the direction of platen.

According to the described clutch pack of one of claim 117-119, it is characterized in that 120, when elasticity loading supporting was mobile, the Separating force of dish stage clip reduced.

According to the described clutch pack of one of claim 117-120, it is characterized in that 121, the displacement distance that elasticity loads supporting should make maximum separation power that acts in the supporting and the reaction force that supporting upward produces reach till the equilibrium of forces.

According to the described clutch pack of one of claim 117-121, it is characterized in that 122, the dish stage clip will have the force characteristic curve of decline at least on the part area of separating stroke.

According to the described clutch pack of one of claim 117-122, it is characterized in that 123, the reaction force that produces in spring-loading supporting is formed by force-storing device, force-storing device has the constant power of substantial constant on set adjustment region.

124, according to the described clutch pack of one of claim 117-123, it is characterized in that having axial elasticity or movably support and load by the dish spring that uses as force transducer.

125, one of require the described friction clutch that is particularly useful for Motor Vehicle according to aforesaid right particularly, has platen, this platen can not rotate but can do and axially limitedly link to each other with shell movably, between shell and platen, be provided with simultaneously a dish spring, by this dish spring platen is subjected to towards the load of the clamped clutch disk direction between platen and opposed platen, and clutch can and separate by the operating device joint, also has a controlling device that can compensate automatically occurring wear on the friction pad of clutch disk at least, it is characterized in that, controlling device has two and is located at same parts (lid, platen) on and at the ring that radially is spaced from each other certain distance, two rings are in controlling device, for example can move axially towards the dish spring under the effect of sloping platform formula device, regulating device then can reverse producing on tangential under the effect of conveying equipment.

According to the described friction clutch of one of claim 1-125, it is characterized in that 126, when friction clutch was in jointing state, the dish spring also stoped the controlling device generation to be reversed with first ring that its first radial portion supports as the wear compensation ring thus.

127, according to the described friction clutch of one of claim 1-126, it is characterized in that, second ring is that the regulating device of abrasion detection ring is provided with a stopping device that has sensor and can avoid reversing, the effect of stop will be cancelled when friction clutch is in jointing state and wearing and tearing take place, and can second ring be produced with the corresponding axial displacement of wearing and tearing by suitably reversing of controlling device thus and then make stopping device bring into play its effect in separation process.

128, according to the described friction clutch of claim 125-127, it is characterized in that, when appearance is worn and torn in the separation process, after the rotation of second controlling device of encircling that correspondingly takes place in advance, in order to make the first controlling device rotation that encircles and it to be discharged from stopping device.

According to one of aforesaid right requirement described friction clutch, it is characterized in that 129, ring itself has sloping platform and be provided with the force-storing device that works on tangentially.

130, according to the described friction clutch of one of claim 1-129, it is characterized in that, when the gradient of dish spring changes because of wearing and tearing, make the effect cancellation of stopping device.

131, according to one of aforesaid right requirement described friction clutch, it is characterized in that, when the axial position that makes platen because of wearing and tearing changes, make the effect cancellation of stopping device.

132, one of require described friction clutch according to aforesaid right at least, it is characterized in that controlling device generation effect between clutch lid and dish spring.

According to the described friction clutch of one of claim 1-131, it is characterized in that 133, controlling device is the generation effect between dish spring and platen.

134, according to the described friction clutch of claim 132, it is characterized in that, in the axial arrangement space, controlling device is arranged between clutch cover plate and the dish spring.

135, according to the described friction clutch of claim 133, it is characterized in that, in the axial arrangement space, controlling device is arranged between dish spring and the platen.

136, one of require described friction clutch according to aforesaid right at least, it is characterized in that, two rings by torsion proof in the friction clutch but can do axially movable parts for example platen support.

137, one of require described friction clutch according to aforesaid right at least, it is characterized in that, two rings by the Axial Mounting Part in the friction clutch for example cover plate support.

138, one of require described friction clutch according to aforesaid right at least, it is characterized in that sensor formation stopping device itself.

139, a kind of friction clutch is characterized in that, the effect of stopping device strengthens with the separation process of friction clutch relevantly.

140, one of require described friction clutch according to aforesaid right at least, it is characterized in that, when friction clutch is in jointing state, permission is made of the extension member that at least one has axial elasticity at the wear sensor that reverses and the abrasion detection ring is axially adjusted with respect to the gradient or the axial position variation of cover plate according to platen on tangential by controlling device, when friction clutch is in jointing state and new state, under the state that controlling device adjusts accordingly wearing and tearing, this elastic component is bearing on the clutch component and second ring with such component, what promptly the effect of inertia by the feedway that works on tangential and ring prevented that the environment-development life from reversing and causing thus moves axially, and when friction clutch was in jointing state and because of wearing and tearing the axial position of the gradient of dish spring or platen is changed, the Support of sensor was reduced pressure second ring at least or is mentioned and make ring reverse and produce thus from feedway and moves axially.

141, according to one of aforesaid right requirement described friction clutch, it is characterized in that sensor is made of leaf spring or dish spring type elastic member.

According to the described friction clutch of claim 141, it is characterized in that 142, sensor is made of flexible parts with precompression.

According to the described friction clutch of claim 142, it is characterized in that 143, sensor is fixed on the dish spring.

144, one of require described friction clutch according to aforesaid right at least, it is characterized in that a radial portion of sensor is hinged with the dish spring, and another radial portion is bearing in second and encircles.

145, one of require described friction clutch according to aforesaid right at least, it is characterized in that, sensor with its 3rd regional additional support on the dish spring.

146, one of require described friction clutch according to aforesaid right at least, it is characterized in that, sensor is fixedly hinged at lid, and links by the limiting area of shell on second ring on opposite, Support, and is relative with the Support with the distance L that can overlap when separating herein.

147, according to one of aforesaid right requirement described friction clutch, it is characterized in that sensor is arranged on the abrasion detection ring.

148, according to the described friction clutch of claim 147, it is characterized in that, the sensor that has a wear detector by two parallel and in the axial direction each other the ring of elastic tension constitute.

149, one of require described friction clutch according to aforesaid right at least, it is characterized in that the abrasion detection ring is made of elastic member.

150, according to one of aforesaid right requirement described friction clutch, it is characterized in that the abrasion detection ring is made of corrugated spring forming spare.

151, one of require described friction clutch according to aforesaid right at least, it is characterized in that the conveying equipment that is used at least one regulating ring is made of spring.

According to the described friction clutch of claim 151, it is characterized in that 152, spring-loaded is having on the parts of ring.

According to the described friction clutch of claim 152, it is characterized in that 153, two spring shackles are connected in series.

154, according to the described friction clutch of claim 153, it is characterized in that, be supported on the ring bearing parts with one of first or second ring corresponding spring, and with first or second ring in another encircles corresponding spring and is supported on the ring.

155, according to the described friction clutch of one of claim 151-154, it is characterized in that, ring is supported on the spring of the power of a spring on the ring bearing parts greater than another ring.

156, according to the described friction clutch of above-mentioned at least one claim, it is characterized in that, by be located on second ring and make opposite opposed spacing preiection and constitute this braking device from cutting the projection that looks up with the first ring heel, it just discharges first ring and rotates after rotation is given birth in second environment-development.

157, one of require described friction clutch according to aforesaid right at least, it is characterized in that when clutch was in separated state, second ring was lockable and can not reverses.

158, one of require described friction clutch according to aforesaid right at least, it is characterized in that, when friction clutch is in jointing state, have an axial distance L that can overlap between the limiting area of second ring and parts, between the parts and second ring axial relative movement can take place in separated state.

According to the described friction clutch of claim 157, it is characterized in that 159, the dish spring encircles second in the state lower support of separating rotation.

According to claim 157 or 158 described friction clutches, it is characterized in that 160, second ring is pressed to lid under separated state.

161, according to one of aforesaid right requirement described friction clutch, it is characterized in that, be arranged on the ring of second on the platen and under separation and axially movable state, press to the dish spring.

162, according to one of aforesaid right requirement described friction clutch, it is characterized in that, be arranged on the ring of second on the pressing plate and press down to shell in the separation and the state that moves axially.

According to the described friction clutch of one of claim 1-162 at least, it is characterized in that 163, the distance L 1 between dish spring supporting on the axial distance L2 of first ring and second ring and first ring and the dish spring on the relative parts support is in a ratio of L2＞30%L1.

According to the described friction clutch of one of claim 1-163 at least, it is characterized in that 164, the radial distance between first ring and second ring is approximately equal to supporting of dish spring and the distance between the dish spring supporting on the parts relatively on first ring at least.

165, according to the described friction clutch of claim 1-164, it is characterized in that the approximate at least ventilation stroke (L1) that is equivalent to clutch pressure plate of the springing stroke of sensor (L).

166, according to the described friction clutch of one of claim 1-164, it is characterized in that the ventilation stroke S of the springing stroke S of sensor and clutch pressure plate _DRatio be S＜=S _D* (L2: L1) (Figure 72).

167, one of require described friction clutch according to aforesaid right at least, it is characterized in that, so-called draw-off type clutch has had the dish spring of single-arm lever effect and has been arranged on second ring of the first ring radially inner side, and two rings all be arranged between dish spring and the lid axially on.

168, require one of 1-167 described friction clutch according to aforesaid right at least, it is characterized in that, so-called draw-off type clutch has had the dish spring of single-arm lever effect, and second ring is arranged on the radial outside of first ring, wherein two rings all be arranged between dish spring and the platen axially on.

169, according to the described friction clutch of one of claim 1-160 at least, it is characterized in that, so-called pressure type clutch has had the dish spring of double-arm lever effect and second ring has been arranged on the radially inner side of first ring, two rings all be arranged between dish spring and the platen axially on.

170, according to the described friction clutch of one of claim 1-160 at least, it is characterized in that, so-called pressure type clutch has had the dish spring of double-arm lever effect and the radial outside that second ring is arranged on first ring, and wherein two rings all be arranged between dish spring and the dish axially on.

171, one of require described friction clutch according to aforesaid right at least, it is characterized in that the opposed sloping platform of controlling device is to be made of the sloping platform that is compressed on the clutch lid.

172, according to the described friction clutch of claim 154, it is characterized in that, between each sloping platform on the lid, be provided with through hole.

According to the described friction clutch of claim 169, it is characterized in that 173, the opposed sloping platform of controlling device is to be made of the sloping platform that is formed on the platen.

According to the described friction clutch of claim 173, it is characterized in that 174, the sloping platform on the platen forms by suppress each sloping platform on a plate-like piece.

175, according to the described friction clutch of claim 174, it is characterized in that, at platen with have and be provided with the passage that radially extends between the plate-like piece of sloping platform.

176, one of require described friction clutch according to aforesaid right at least, it is characterized in that ring is that the wear compensation ring has the pivoting support that is used for the dish spring simultaneously.

177, according to the described friction clutch of one of claim 1-172, it is characterized in that, on clutch with pressuring method work, controlling device is arranged between dish spring and the lid, a side that allows regulating device to rotate thereon on the dish spring is supported by support spring.

According to one of aforesaid right requirement described friction clutch, it is characterized in that 178, when clutch separation, supporting dish spring provides a pivoting support position in the phase I of separating stroke for the dish spring.

179, according to the described friction clutch of claim 178, it is characterized in that, after the outer rim of dish spring kept flat on the detection ring and separating in the second stage of stroke bearing and turning on the detection ring, the dish spring was mentioned and is made supporting dish spring produce resiliently deformable in the direction of platen from the supporting of first ring.

According to the described friction clutch of one of claim 1-176, it is characterized in that 180,, in clutch, controlling device be arranged between dish spring and the platen that platen is by spring and lid tension.

181, a kind of friction clutch that is specially adapted to Motor Vehicle, it has platen, this platen can not rotate but can move axially with an Axial Mounting Part for example shell link to each other, between shell and platen, acting on simultaneously a dish spring, can apply towards the load of the clutch disk direction that between platen and opposed platen, can clamp to platen by the dish spring, and can make clutch and separate by control mechanism, also has at least the controlling device that can compensate automatically occurring wear on the friction pad of clutch disk, it is characterized in that controlling device is arranged between clutch lid and the dish spring.

182, particularly according to one of the aforesaid right requirement described friction clutch that is particularly suitable for Motor Vehicle, has a platen, this platen can not rotate but can move axially with an Axial Mounting Part for example shell link to each other, between shell and platen, acting on simultaneously a dishful of spring, can apply towards the load of the clutch disk direction that between platen and opposed platen, can clamp to platen by the dish spring, and can make clutch and separate by control mechanism, also has at least the controlling device that can compensate automatically occurring wear on the abrasion pad of clutch disk, it is characterized in that, controlling device has two rings that radially separate and that be provided with one heart mutually, two rings under the effect of the sloping platform device that regulating device for example is made of sloping platform and opposed sloping platform can the dish spring axially on move, controlling device can rotated on tangential under the effect of feedway, when clutch is in jointing state, it is on the wear compensation ring that first radial portion of dish spring is supported on first ring, and stop controlling device to be reversed thus, second ring is that the effect of the controlling device of wear compensation ring can be interrupted by stopping device, this stopping device has a sensor, and can be by will on second ring, preventing that regulating device from reversing in a zone of leaving first radial portion from self-supporting, when wearing and tearing and friction clutch occurring and be in jointing state, the effect of this stopping device should reduce at least, can second ring be produced with wearing and tearing by suitably reversing of controlling device thus moves axially accordingly, and when clutch was closed, the effect of stopping device strengthened.

183, particularly according to one of aforesaid right requirement described friction clutch, this clutch is particularly useful for Motor Vehicle, this clutch has a platen, platen can not rotate but can do and axially limitedly link to each other with shell movably, between shell and platen, acting on simultaneously a dish spring, can apply load to platen by this dish spring towards the clutch disk direction that can between platen and opposed platen, clamp, and can make clutch and separate by an operating device, can be when on the friction disk of clutch disk, wearing and tearing occurring at least but also have to its controlling device that compensates automatically, it is characterized in that, combined to two features that the major general is following, that is:

Controlling device has the ring that two footpaths upwards are spaced from each other setting, two rings controlling device for example under the effect of sloping platform device can the dish spring axially on move, controlling device can rotated on tangential under the effect of feedway,

When clutch was in jointing state, it was on the wear compensation ring that first radial portion of dish spring is supported on first ring, and prevented the controlling device rotation thus,

Second ring is that the effect of the controlling device of abrasion detection ring can be interrupted by the stopping device that possesses sensor and prevent to reverse, can be cancelled when wearing and tearing and clutch are in jointing state appears in the acting on of this stopping device, can second ring be produced with wearing and tearing by suitably reversing of controlling device thus moves axially accordingly, stopping device is played a role

When occurring wearing and tearing along with the continuation of separation process, the controlling device of first ring discharges from braking device in order to reverse, and that carries out after this and correspondingly before this that second controlling device of adjusting ring carried out reverses.

184, according to one of the aforesaid right requirement described friction clutch that uses with clutch disk, it is adapted to Motor Vehicle especially, wherein clutch has a rotating support that is used for the dish spring, the dish spring applies towards the load of pressure disk and opposed platen direction to axially movable platen, and has a device that can compensate the wearing and tearing of friction plate at least, it is characterized in that, at least approximate from clutch disk on detaching direction no longer or only apply the stroke of inappreciable load to platen, the power of dish spring and another force-storing device is superimposed, and the distribution curve of making a concerted effort that obtains is thus compared with the power distribution curve of dish spring remain basically stable.

According to the described friction clutch of one of claim 1-184, it is characterized in that 185, clutch disk is one and has the clutch disk of " pad spring ".

According to the described friction clutch of one of claim 1-185, it is characterized in that 186, another force-storing device is an all-in-one-piece in clutch " counterbalance spring ".

According to the described friction clutch of one of claim 1-186, it is characterized in that 187, counterbalance spring is a dish spring.

188, according to the described friction clutch of one of claim 1-187, it is characterized in that, at least approximate from clutch disk on detaching direction no longer or only apply the stroke (release travel) of inappreciable load to platen, counterbalance spring has the power-flight distribution curve of a bending, this curved section all deviates from mutually with the bending of the power-flight distribution curve of dish spring, and for example direction is opposite.

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