CN101163904A

CN101163904A - Wheel brake

Info

Publication number: CN101163904A
Application number: CNA2006800133331A
Authority: CN
Inventors: G·多韦; M·佩勒; C·阿布特
Original assignee: BPW Bergische Achsen KG
Current assignee: BPW Bergische Achsen KG
Priority date: 2005-04-20
Filing date: 2006-04-19
Publication date: 2008-04-16
Anticipated expiration: 2026-04-19
Also published as: CN100552253C; CN101163903A; CN100552254C; DE102005018157B4; DE102005018157A1

Abstract

The unit comprises a plunger (2) moved inside a housing (1) towards the brake pad, a device activating the plunger (2) and an adjusting element (10) positioned between the plunger (2) and the activating device. A nut (22) maintains the information about the first moving distance in a particular position, which is transmitted to the adjusting element (10) after returning to its prior position. The plunger (2) is moved in relation to the adjusting element (10). A spindle (21) and a spring-loaded clutch between the nut (22) and the adjusting element (10) are also incorporated.

Description

Wheel drag

Technical field

The present invention relates to a kind of according to claim 1 wheel drag as described in the preamble.

Background technique

Described disk type braker in many open source literatures, they also are provided with regulating device except the braking hold down gag, are used for the wearing and tearing by compensation brake strip of the spacing between adjusting brake strip and the brake disc and/or brake disc.

By the known a kind of disk type braker of DE 2925342 A1 with pure regulating device of mechanically working.For the brake activation device, a pressure plunger is applied in pressure together with a nut and the press member with outside helical teeth portion by a hold down gag, and pressure plunger, nut and press member are moved to the direction of brake strip jointly.Affiliated regulating device extends transverse to the movement direction of pressure plunger.The chief component of regulating device is to adjust axle, and it is provided with helical teeth portion on its circumference, and it is corresponding with the helical teeth portion that constitutes on the circumference of nut.The member that is provided with transverse to the movement direction of pressure plunger equally of other of helical teeth portion by these two correspondences and regulating device, for example sleeve, nut, helical spring etc. cause actual adjustment effect.This wheel drag has the bigger structural type of floor space.

Summary of the invention

In order to create a kind of wheel drag that is used for the integrated regulating device of having of automotive wheel, it is characterized in that the compact structure form, advise a kind of wheel drag according to the present invention with feature given in claim 1.

In this wheel drag and particularly disk type braker, integrated regulating device mechanically and with the energy and the signaling system of automobile self is irrespectively worked, and it is characterized in that compact structural type.

Particularly advantageously for the compact structure of wheel drag be, the pressure plunger is a double-plunger, and two single plunger is connected to each other rigidly by a york piece, comprises that adjusting being threaded of element is positioned at the center of this york piece.

For the described integrated regulating device that after changing old worn out brake strip, can reset, adjust element and can be provided with a tooth portion.

Described tooth portion can be designed so that again it is meshed with a tooth portion that is arranged on the gear of adjusting the element next door.On this gear, there is geared assembly then, is used to adjust resetting of element.Preferably, this gear can be rotated to support on the extension of a side direction of first pressure elements.

Description of drawings

Explain the different forms of implementation of wheel drag below with reference to accompanying drawing.In the accompanying drawing:

Fig. 1 comprises the sectional view of brake calipers of the wheel drag of brake disc and brake strip,

The view that Fig. 2 only illustrates (it is roughly corresponding to the section II-II among Fig. 1) shows the theory structure of regulating device;

Fig. 3 shows the principle of regulating device with the different stage (Fig. 3 a to 3e),

Fig. 4 presses another embodiment of regulating device of the present invention,

Fig. 5 is along the phantom of Fig. 4 midship section V-V,

Thin portion shown in the strong method among Fig. 5 a Fig. 5,

The sectional view of the section VI-VI of Fig. 6 in Fig. 5,

The decomposition view of the thin portion of the controlling device among Fig. 7 Fig. 5,

Fig. 8 presses another embodiment of regulating device of the present invention,

Thin portion shown in the amplification among Fig. 9 Fig. 8,

The decomposition view of some thin portions of the regulating device among Figure 10 Fig. 8,

The sectional view of the brake calipers of another form of implementation of Figure 11 disk type braker,

Thin portion shown in the amplification of Figure 12 Figure 11, and

Another thin portion shown in the strong amplification of Figure 13 Figure 11.

Embodiment

Fig. 1 shows the simplification view of a part of brake shell 1, the 1a of the automotive disc brake of preferred floating brake calipers structural type.Two pressure plungers 2 interconnect by a york piece 2a who extends transverse to the pressure plunger in brake shell 1 inside.Therefore these two pressure plungers 2 as Fig. 2 very schematically can find out, have formed a double-plunger, its at the external support of brake shell 1 on the back side of the cladding plate 3 of brake strip 4.Except that brake strip 4, in Fig. 1 and 2, also illustrate in the friction covering 5 respectively, and the brake disc 6 of disk type braker in addition.

The pure regulating device of mechanically working that is in operation and below the disk type braker of the both sides of brake disc 6 work is provided with, also will explains in more detail with air gap L (Fig. 2).Though it is configured to make it to have only one still to adjust two pressure plungers 2.

In order to transmit the impacting force that is produced by the air-controlled master cylinder of master cylinder and preferred compressed, but a brake lever 13 is installed on deflection ground in brake shell 1.On the lever free end of representing with A, can support the operating handle 7 of the master cylinder that schematically illustrates.If this master cylinder is loaded pressurized air, then lever 13 is around fixing bearing 66 deflections of itself and shell.At this, cause two pressure plungers 2 to move simultaneously to the direction of brake disc 6 by the

pressure elements

60,59 of centre connection with the york piece 2a that each pressure plunger is rigidly connected to each other vertically.The details of bearing and support also will be set forth below in more detail.

According to Fig. 2 that ten minutes principle shape is represented, dual pressure plunger 2 is provided with internal thread at the center of its york piece 2, and it is formed on to adjust with outside thread of adjusting element 10 and is threaded 11 between element 10 and the pressure plunger 2.The adjustment element 10 that is arranged on center between the pressure plunger 2 of each rigidity with particularly saving the space by this way be designed to jar shape and within it portion comprise each discrete component of regulating device.

Hold down gag can for example be a compressed-air controlled, and clamping lever 13 is applied to active force on the adjustment element 10 by the member that the centre connects thus.Realize continuing equably to be transmitted on two pressure plungers 2 by adjusting element 10, and cause the feed movement of brake strip 4 thus with respect to brake disc via 11 impacting forces that are threaded.

Be supported on the swing link 14 to the hinge 61 rotatable motions of clamping lever 13 by a bowl-type.The spin axis of bowl-type hinge 61 is parallel to but dislocation is extended in the spin axis ground with the fixing bearing 66 of shell, and york piece 2 is parallel to this two spin axis ground extensions too.

Swing link 14 is supported on the pressure elements 60 by a flat bearing 15 again.Flat swing link 14 has the gap with respect to pressure elements 60 up and down, so that can realize the motion of side direction.

Pressure elements 60 is arranged in the shell 1 like this, makes it non-rotatable with respect to shell 1.For this purpose, pressure elements 60 can be supported on the guiding device of shell 1 internally.

Towards brake disc 6, press member 60 is provided with a spigot edge 134.This spigot edge is columniform at this, and is supported on its distolateral pressure side 60a on the cooperation pressure side 12a of a circle, and this cooperation pressure side is formed on the adjustment element 10 with the form of circular deep gouge.Therefore be in operation, adjusting element 10 can be with respect to pressure elements 60 around center line 62 rotation.The friction that occurs when rotatablely moving in order to be reduced in this, can pressure side 60a with cooperate be provided with between the pressure side 12a one by the Teflon (Teflon: the flat pad of teflon) making, as sliding bearing.

Explain the working principle of integrated regulating device below by Fig. 2, adjusting element 10 is important component parts of this regulating device.Other constituent elements of this regulating device are a screw member 22 and the screw members 21 of pressing the design of nut form by the design of bolt form.The internal thread of screw member 21 embeds in the outside thread of respective design of another screw member 22.The spiral that constitutes like this between two

screw members

21,22 connects 23 and has bigger pitch, as can be seen in FIG..This pitch is particularly obviously greater than 11 the pitch of being threaded of adjusting between element 10 and the pressure plunger 2 formation in the same way jar shape.In addition, spiral connection 23 is designed to rub low-down.

The screw member 22 of bolt type is provided with a cylindrical portion section 24 in the zone of its back end, its guiding in one that adjusts element 10 hole 25 of correspondingly determining size.At its other end towards brake strip 4, screw member 22 is provided with one and reverses stopper and some structures, the axial displacement of their restriction screw members 22.In order to prevent to reverse, this end of screw member 22 is provided with square toes 27, and it passes a corresponding quadrilateral hole among the cover plate 1a of brake shell 1, though and allow axial motion not allow to rotate there.In order to limit the motility of screw member 22, on fixing brake shell 1 cover plate 1a, design one first backstop 28 and one second backstop 29 thereon and correspondingly.Correspondingly obtain one first slit S1 and each second slit S2 (Fig. 3 b).If first screw member 22 is to the direction motion of friction brake wafer 4, then the first axial clearance S1 reduces, until arriving first backstop 28.On the contrary, screw member 22 leaves friction brake wafer 4, and then the second axial clearance S2 is eliminated gradually, limits this axial motion until second backstop 29.

Be provided with the pressure side 30 of a friction clutch towards brake strip 4 according to another screw member 21 of nut form design.By as the pressure side 30 of clutch, the screw member 31 sealed twelve Earthly Branches support that can rub is being adjusted of element 10 as on the cooperation pressure side 31 of engagement clutch.In the present embodiment, pressure side and cooperate pressure side to be designed to annular, and in order to improve the friction on

mating face

30 and 31 is designed to slight taper.

Another, i.e. a side of brake strip 4 dorsad, a pressure spring 33 is supported on the screw member 21.In this embodiment, this pressure spring 33 is belleville springs that surround screw member 22 circlewise.This belleville spring is supported on the thrust-bearing 34 with its other end again, and itself is supported on to be adjusted on the element 10.Among the embodiment shown here, thrust-bearing 34 is rolling bearings.

Second thrust-bearing 36 of a rolling bearing form is supported on the adjustment element 10 and is loaded by pressure spring 37 on the other hand, and it is supported on the brake shell 1 with its other end.This spring 37 is a helical spring that surrounds screw member 22 in the present embodiment.37 on spring is provided with in the centre to act under the situation of thrust-bearing 36 adjusts element 10, thus to adjust element produce lasting but on sense of rotation frictionless axial force almost, set up resetting of its reliable in function thus reliably.

Equally, another pressure spring 33 is supported on the thrust-bearing 34 there, also causes the lasting axial force of double thread element 21, and wherein this axial force also almost is frictionless on sense of rotation.On the contrary, by pressure side 30 with to cooperate the friction of the friction clutch that pressure side 31 constitutes be bigger,, screw member 21 adjusts on the element 10 as long as supporting to.Pressure side 30 and cooperation pressure side 31 are constituent elements of clutch mechanism thus, this clutch mechanism can be set up being connected or these two component groups are synthesized a unit between the internal thread of the outside thread of adjusting element 10 and screw member 21, wherein this connection can be eliminated on the other hand again, makes these two members to rotate relative to one another.Screw

member

21,22 and adjust element 10 and is provided with one heart, this causes the mode of structure in the pressure plunger 2 of being integrated in of compactness.

Set forth the function of regulating device below by Fig. 3 a to 3e.

Fig. 3 a illustrates the state of rest of break after manipulation, and the wearing and tearing V of friction brake wafer has taken place in manipulation, therefore will proceed to the adjustment of small part in braking process next time.In the friction covering 5 and brake disc 6 between distance here obtain with the size sum of the wearing and tearing V that will compensate by desired air gap L.

According to Fig. 3 b, when braking process begins, under the effect of impacting force F, adjust element 10 and be moved to the direction of brake disc 6 and against the power of spring 37 together with two

screw members

21,22 and pressure plunger, lean on brake shell 1 until the backstop 28 of first screw member 22.This position is shown in Fig. 3 b.As Fig. 3 b can find out, to have reached size be zero to first axial clearance on this position, and the opposite second axial clearance S2 has reached its maximum value.

Continue to be loaded impacting force F in order to overcome wearing and tearing V now if adjust element 10 by Fig. 3 c, it is with respect to being moved by first screw member 22 of axial locking now so, and pressure plunger 2 is close to cladding plate 3 simultaneously.Rise from the cooperation pressure side 31 of adjusting element 10 because it is connected with another screw member 22 at this screw member 21.Effect by spring 33 with because spiral is connected 23 large screw pitch, screw member 21 freely turns clockwise with respect to fixing screw member 22, makes it be driven by spring 33 and revolves again on the cooperation pressure side 31 that comes to adjustment element 10.Screw member 21 is under the state that rises and adjust that element 10 is the same does identical axial motion, abuts on the brake disc 6 after brake strip 4 is overcoming the V that weares and teares.This position is shown in Fig. 3 c.When compressing end, the mating face 31 of adjusting element 10 is expressed to again securely by first pressure spring 33 on the mating face 30 of second screw member 21, and screw member 21 and adjustment element 10 engage again thus.

Impacting force F cancels (shown in Fig. 3 d) along with the end of braking process.By the active force of pressure spring 37, at first whole regulating device is communicated with pressure plunger 2 to be retracted, and bumps against with its backstop 29 on the brake shell 1 that forms immovable point until screw member 22.Screw member 22 from this constantly by locking in case the past swivel motion that continues.

Adjust element 10 toward the process of swivel motion in pressing Fig. 3 e, the size of the active force of elastic spring 37 is enough to make screw member 21 and adjusts element 10 and rotate with respect to the screw member 22 of axial locking as a whole and counterclockwise then, shown in Fig. 3 e.By being threaded 11, in the time of with 10 rotations of adjustment element, york piece 2 and two pressure plungers 2 are moved or adjust, and are the directions to brake disc 6.

By the restricted movement of screw member 22 between its first terminal backstop 28 and its second terminal backstop 29, therefore can be based upon the desired air gap between brake strip 4 and the brake disc 6, perhaps this air gap is adjusted continuously in that disk type braker is in service.Two

backstop

28,29 as immovable point is arranged in the area B of brake shell 1 (comparison diagram 2) in the present embodiment, and this zone is between brake strip and regulating device.Because do not have as far as possible because the casing deformation of braking force at this area B inner brake shell.Therefore almost unavoidable in practice distortion so can not exert an influence to the precision of adjusting.At the opposite side of brake disc 6, the air gap there also must be eliminated by above-mentioned adjustment, because brake strip there also is worn.

By be threaded 11 and the ratio of that pitch of 23 of being threaded predetermined, which kind of degree abrasion size is compensated to or how far pressure plunger 2 is moved to the direction of brake disc 6 with respect to adjusting element 10 in braking process.For example, being adjusted on a plurality of braking processs of the wearing and tearing V of generation adjusted.

Another form of implementation that is used for the regulating device of disk type braker is described by accompanying drawing 4 to 7 below.In order to describe this form of implementation, Fig. 5 a that has the terminal backstop that realizes by screw thread is a particular importance.

Fig. 4 schematically illustrates the york piece 2a that two pressure plungers are rigidly connected to each other, and it is again according to the design of the form of crossbeam, and extends or extend to this figure paper plane from the figure paper plane in the view of Fig. 4.Adjust element 110 and be seen as the profile of mushroom-like roughly from the side and have outside thread on the major part of its length, it constitutes together with the corresponding outside thread of crossbeam or york piece 2a and is threaded 111.Compressing the end of side, regulating device has screw member 122, and it is as pressure elements.Constitute the pressure side 112 of a pit-shaped thereon, roughly semi-cylindrical groove just, it is parallel to york piece 2a extends, and rotatable motion ground supports clamping lever, for example clamping lever shown in Fig. 1 on this groove.In this way, impacting force F is passed on the screw member 122 that is designed to pressing plate.In addition as can be seen from Figure 4, adjust element 110 and be provided with an outer toothed portion 129 for resetting of regulating device.Also its function to be described after a while.

Fig. 5 combines the primary component that regulating device is shown with sectional drawing with Fig. 5 a,, adjusts element 110 itself, first screw member 121, another screw member 122, two sleeves 125,126, overrunning clutch 138 and torque clutch 139 that is.A gear 140 that is used to reset when brake strip is changed additionally also is shown.These parts illustrate to analyse and observe in Fig. 5.Only be not first screw member 121 that is designed to centre bolt to analyse and observe what illustrate.It is fixed with respect to the cover plate 1a of brake calipers or brake shell like this by its end, though the screw member 121 of winning is not moved in the axial direction, can be around the axis rotation of himself.The cover plate 1a of brake shell 1 is provided with the 1b of indentation portion that provides shape sealed in the place that bolt shape screw member 121 supports.The 1b of this indentation portion has avoided the perforate there among the cover plate 1a, can arrive the inside of brake shell 1 by this perforate dust.

At its other end, screw member 121 is provided with the external thread section 121a of a large screw pitch.But another screw member 122 axial motion and the braking force when form borrowing it compressing simultaneously in the brake calipers shell are delivered to that pressing plate of adjusting on the element 110.Be threaded in order to form, being threaded as shown in Fig. 5 a, another screw member 122 has internal thread segment 122a, and the external thread section 121a of screw member 121 embeds among this internal thread segment 122a.Being threaded of constituting like this 123 has one and 111 compares big pitch with being threaded.In addition, be threaded and 123 between two backstops that constitute like this, have an axial thread pitch S3 (Fig. 5 a).This thread pitch S3 roughly is equivalent to desired air gap L dimensionally.

By introducing braking process, that is when the pressure side 112 of double thread element 122 applied impacting force F, this screw member and the adjustment element 110 that axially seamlessly reclines were thereon driving via the 111 direction motions that are fixed under the situation of adjusting the pressure plunger 2 on the element 110 to brake disc that are threaded.At this, impacting force F at first also is not passed on the screw member 121 at center.

Impacting force is to more precisely only just generation after air gap S3 eliminates of the transmission of screw member 121, in case promptly the tooth side of the internal thread of screw member 122,121 and

outside thread

121a, 122a enters the words that recline mutually.Axially the tooth side 150,151 of not movable screw member 121 is formed for the terminal backstop of axial movable screw member 122 at this, screw member 122 can axially reciprocating with respect to screw member 121 between each terminal backstop, and can not cause rotatablely moving of screw member 121.But since the screw member 122 of axial motion with can not the screw member 121 of axial motion between steeper be threaded 123, screw member 121 begins rotation under the effect of impacting force, in case screw member 122 has reached one of them terminal backstop, be the words of the tooth side 151 of screw member 121.

Force at rotatablely moving of screw member 121 like this, and in being delivered to via overrunning clutch 138 on direction therein on the cover 126 corresponding to brake wear, promptly in cover 126 follow the rotation of screw member 121 therein on sense of rotation.And overrunning clutch is not worked on opposite sense of rotation, and screw member 121 can rotate freely with respect to interior cover 126.Free wheel device or also have serpentine spring (Schlingfeder) can be used as overrunning clutch 138 for example.

Selectively, in the route between overcoat 125 and interior cover 126 or the line of force overrunning clutch/free wheel device can be set.

Rotation shape by polygonal guiding device 127 forms is sealed, and the guiding in short overcoat 125 like this of interior cover 126 makes the rotation jointly all the time of overcoat and interior cover 125,126 to move axially on the contrary between two sleeves 125,126.This polygonal guiding device 127 here is the Hexagon guiding device, on cover 126 the outside and correspondingly also be molded on the inboard of overcoat 125, this is seen also Fig. 6 and 7 in it is molded over.

The cross section of the overcoat 125 that is loaded by axial pressure by spring 137 is jar shape roughly, and wherein jar bottom surface towards pressure spring 137 has a center drilling that is used to pass screw member 121.The bottom surface of overcoat 125 is at the distolateral groove 132 that is provided with many along its circle distribution, and these grooves 132 constitute bearing housing with being positioned at the opposed groove of adjusting on the element 110 132, are used to be positioned at spheroid 130 wherein.Spheroid 130 is combined among the common ball bearing retainer 130a (Fig. 7).

From opposite side, overcoat 125 is loaded spring force via pressure spring 137, and it remains on its bearing housing 132 inside with spheroid 130 by common mode.Pressure spring 137 gets on the end of overcoat 125 dorsad at pressure spring by low rolling bearing 131 axially support of frictionally working.In this way, spring 137 is constituent elements of torque clutch 139 with spheroid 130, thereby this torque clutch makes adjustment element 10 depend on that torque ground also engages with screw member 121 at last with overcoat 125.Here, rotatablely moving of screw member 121 and overcoat 125 only just is passed to the housing 113 of adjusting element 110 until a definite torque limit values (degree of depth that it depends on the spring constant of pressure spring 137 and is used for the groove 132 of ball), and york piece 2a is adjusted by 111 directions to brake disc that are threaded thus.If the torque value of overstepping the extreme limit on the torque clutch 139, for example when brake strip clinged on the brake disc, then ball 130 left its groove 132, and pressure spring 137 is compacted, and overcoat 125 rotates with respect to housing 113.This result who causes is that rotatablely moving of screw member 121 is not passed on the adjustment element 110.The performance characteristic of the spring constant of pressure spring 137 and overload or torque clutch 139 is chosen to, and makes to fill in when making that so far brake strip abuts on the brake disc when pressure column, and this clutch skids then always.

After braking process finishes, promptly to cancel when making stress F, screw member 122 is moved back into home position with adjusting element 110 towards the second terminal backstop by pressure spring 137.

Along with the increase gradually of the wearing and tearing of brake strip, the rotation of crossbeam 2a by adjusting element 110 is via being threaded 111 and little by little to the direction motion of brake disc.Therefore when changing brake strip, regulating device need be resetted to its initial position again.For the assembler is resetted easily, adjust the tooth portion 129 that element 110 is provided with an outside, outer toothed portion 141 engagements of it and gear 140, this gear can be rotated to support in the perforate of extension of a side direction of screw member 122 around spin axis D.Gear 140 can be approaching well from the outside of brake shell for the assembler.

Can finding out among Fig. 6, gear 140 is provided with and is used for for example scarfing device 142 of hexagon head or similar conventional tool of assembly tool as this.Make 110 rotations of adjustment element by swing pinion 140, this adjustment element 111 is deeper rotated among the york piece 2a again by being threaded thus, make crossbeam or york piece 2a enter initial position, on this initial position, the distance between pressure plunger and brake disc is maximum.At this, torque clutch 139 must be crossed, and this can hear well by skidding of ball 130.

For be reduced on the screw member 122 pressure side with adjust element 110 on corresponding cooperation pressure side between the friction that occurs when the relative rotation, the sliding bearing 133 of a pad shape of use between two members.Feel relieved better with respect to adjusting element 110 in order to make pressure elements, a columniform spigot edge 134 that forms the pressing plate 122 of pressure elements is embedded in the circular groove of adjusting a correspondence in the element 110.

In other form of implementation shown in Fig. 8 to 10.The basic structure of this form of implementation still has several structural differences corresponding to the basic structure of Fig. 4 to 7, and following is described these differences.The reference character of each member is corresponding to the above-mentioned form of implementation of pressing Fig. 4 to 7, as long as this member performance identical functions.

In pressing the form of implementation of Fig. 8 to 10, at first, the exchange of the layout of the rolling bearing 131 of pressure spring 37 and axial action.Rolling bearing 131 is supported on the overcoat 125, and pressure spring 137 directly is supported on the caliper component 128.With different in the above-mentioned form of implementation, so spring 137 is not in company with rotation.

Another difference is the support of the bolt shape screw member 121 at the center that is arranged on.This screw member 121 ends at the end of the cover plate 1a of its geared brake shell in globe journal 160.This globe journal 160 is engaged in the spherical mount 161 that is made of plastics.This spherical mount 161 is engaged in the caliper component 128 regularly.In order to reach this fixing cooperation, spherical mount 161 can be provided with an external ribs, and its shape is engaged in the groove that correspondingly designs of caliper component 128 sealedly.Can find out that from accompanying drawing spherical mount 161 surrounds the globe journal 160 of screw member 121 greater than 180 ° of ground on spherical crown.Preferably degree of encirclement is 200 ° to 210 °.In this way, globe journal 160 is fixed and axially pulls out from spherical mount 161 preventing, globe journal 160 can be rotated in spherical mount 160.This rotation realizes that by certain friction torque its intensity depends on the material pair of globe journal/spherical mount.The size of this friction and thus center screw member 121 during around the rotation of its longitudinal axis little resistance be predetermined tolerance accurately.

Another particularity by the form of implementation of Fig. 8 to 10 is, with the configuration of the interior cover 126 of above-mentioned form of implementation reduced in comparison, cover is guided in overcoat 125 via polygonal guiding device 127 in this.Interior cover 126 is long as overrunning clutch 138.In addition should in cover 126 also be permanently connected with housing 164 rotation of overrunning clutch 138, for example by a kind of slight press fit.

Fig. 9 is illustrated in the thin portion of overrunning clutch 138 used herein.The housing that passes through guard ring 168 axial restraints 164 of this overrunning clutch surrounds three longitudinal components, the part in the middle of the locking body 165 of overrunning clutch is arranged in.A plurality of rolling elements 166 are arranged in the part on the left side, and described rolling element does not almost have and frictionally is bearing in this zone, and can not produce the locking effect on one of two sense of rotation.The longitudinal component on the right is admitted a friction ring 167 in Fig. 9.This friction ring produces the low but friction that can accurately reproduce between the screw member 121 at overrunning clutch and center.This friction ring 167 preferably is made of plastics for this purpose.This friction low but that can accurately reproduce helps to adjust the accurate adjustment of element fatefully.Prevented that the zitterbewegung in the vehicle brake emerged in operation from may influence each element of regulating device.

An other form of implementation has been shown among Figure 11.The structure of this form of implementation is very similar to by the form of implementation of Fig. 2 or by the form of implementation of Fig. 3 a to 3e, but it provides on the structure and the advantage on the manufacturing process.Go up cooperation one at screw member 22 (its axial motion is restricted again with S2 by axial clearance S1) here and be designed to relative long sleeve 50, the long especially matching thread that is designed to that it also admits spiral to connect in this way with big helical pitch.Screw member 21 is rigidly connected with sleeve 50 then.The sleeve 50 of screw member 21 can be realized that external screw-thread element 21 special friction on internal whorl element 22 is low and not have stuckly and rotate.

Be different among Fig. 2, the layout of pressure side 30 with the cooperation pressure side 31 of adjusting element 10 of external screw-thread element 21 also is shown in Figure 11.Cooperating pressure side 31 here is not integrally to be positioned to adjust on the element 10 yet, but is positioned on the inserts that is provided with step 51 of an annular.These inserts 51 axially support are on a step, and the inner wall of adjusting element 10 is provided with this step.The also enough rotations of this inserts 51 are arranged on regularly and adjust in the element 10 in addition.The inserts 51 of adjustment element 10 brake disc dorsad has the pressure side 31 of cooperation, and this inserts 51 is provided with an end face 52 towards brake disc, and thrust-bearing 36 is supported on this end face.Support a dihedral ring 52 on thrust-bearing 36 again, it admits the substrate of pressure spring 37.Be designed to have the dihedral ring of shaping cylindrical portion section thereon by it, this ring 52 can make pressure spring 37 centerings, makes that this pressure spring can be not crooked or trackslip.Each parts of pressure spring 37 axial restraints, i.e. inserts 51, thrust-bearing 36 and dihedral ring 52.

In addition, what help structurally to simplify regulating device is, the adjusting of important axial clearance S1 and S2 is undertaken by nut 53, it be screwed on the threaded journal 54 on the end of internal whorl element 22 and there rotation be fixed on regularly on the corresponding position.At this, the bottom surface of nut 53 is as the second terminal backstop 29.

According to Figure 11, adjust element 10 and form the pressure elements 59 that has the cooperation pressure side 12a that constitutes thereon at its end towards hold down gag.Cooperate pressure side 12a to be designed to conical with respect to the center line 62 of regulating device here.The pressure side 60a that the correspondence of pressure elements 60 constitutes abuts on the cooperation pressure side 12a that adjusts element 10, and pressure elements 60 is connected with the clamping lever 13 of hold down gag by hinge 61 rotatable motion ground itself.The pressure side 60a of pressure elements 60 here is conical, and as the conical cooperation pressure side 12a of second pressure elements 59.

Especially, two

pressure side

60a, 12a coaxial in regulating device center line 62 and form an axial slip and thrust-bearing in such a way.This advantage that has is can rotate around center line 62 with respect to pressure elements 60 at the pressure elements 59 of adjusting moulding on the element 10.In addition, as long as transmit pressure, these parts are centering mutually just.Bring big advantage to be equally, be designed to conical 12a, 60a here and when retracting clamping lever 13, also reliably be separated from each other again, make that no longer including frictional force after so separately is applied to respect to it on rotatable adjustment element 10 by pressure elements 60.This brings big advantage in the scope of the regulating device that elaborates in the above, and its prerequisite is the low revolving ability that rubs as far as possible.

The hinge 61 that is designed to monomer or multi-hull type with pressure elements 60 with pressure with preferably also be connected with clamping lever 13 with pulling force.It is positioned on the center line 62 of regulating device and its axis and center line 62 intersect vertically.In addition, this hinge 61 is made up of the hinge bodies 63 and two and half shells of a circle.One of them half shell is positioned on that main body that constitutes pressure side 60a thereon and another half shell constitutes at clamping lever 13.

On the elongation line of hinge 61, clamping lever 13 is supported on the brake shell 1 by bearing 66.In an illustrated embodiment, this bearing 66 is made up of rolling element 67a, the 67b of pref. cylindrical.

Rolling element

67a, 67b roll between first raceway 68 of the supporting pit form of the circular bend of brake shell 1 and second raceway 69 on the clamping lever 13.The displacement of rolling element limits by backstop 67c.

The outer raceway 68 that is designed to support pit has the circular arc bending.The profile of raceway 69 is designed to gradually open on the contrary, and wherein the reference position of this involute is positioned on the center line of hinge 61.Therefore, if clamping lever 13 is deflected by for example master cylinder, then rolling

element

67a, 67b roll on the involute shape profile of raceway 69, apply almost only moving along center line 62 thus on hinge 61, consequently, break feeding under the situation of pressure plunger 2 zero deflections motion.

Figure 12 is illustrated in the raceway 69 and rolling element 67a of the involute shape that constitutes on the clamping lever 13 as the detail drawing of Figure 11, and Figure 13 another rolling element 67b among Figure 11 with the thin portion cross-section illustration of amplifying once more.In addition, these two views illustrate rolling

element

67a, 67b and raceway 69, and this moment, clamping lever 13 was in not deflection state down and be in this situation, that is, clamping lever 13 occupies that it is unsteered, is stress-free neutral position.Inner raceway 69 is provided with one according to the deep gouge of pit form or cave in 70.Compare with all the other levels (Niveau) of raceway, this depression has descended at the amount W shown in Figure 12 and 13.Raceway is designed to radius 71 from 70 transition to normal profile of pit type depression, and rolling

element

67a, 67b move along this profile during feeding.This radius 71 can for example have chamfering radius R.

Figure 12 can find out in two rolling elements, the end position of this rolling element 67a (it takes up position under the situation of not feeding) is limited by delimiting projection 73, this demarcations projection its dorsad terminal qualification of another of radius 71 cave in 70 and obviously protrude in normal profile of raceway 69.This demarcation projection 73 is formed for the terminal stop of determining of the rolling element 67a that is correlated with in this way.

When the break feeding, the yaw motion of clamping lever 13 causes, and rolling element 67a also at first rolls out from its depression 70 as another rolling element 67b.This causes owing to depression 70 degree of depth W produces immediately feeding.In other words, the initial deflection that clamping lever 13 is little at the A place has just caused bigger initial feeding.This bigger initial feeding is owing to the depression in the raceway profile 70 provides big real advantage.Because when feeding begins, also there is not braking force to overcome, but the reposition force of the internal friction of the parts that in this stage, only participate in to some extent, pressure spring 37 and adjust power in case of necessity and will overcome.Therefore the advantage that produces is, for this initial feeding displacement, in order to eliminate air gap L, carries out work with clamping lever 13 big less yaw motions of reaction stroke while.In addition, the aerobraking cylinder that is used in the break feeding now has the performance characteristic of gradually falling when reaching its maximum piston stroke, and this range even is not just to reach by above-mentioned measure.Move the working zone of the piston stroke of being utilized therefore advantageously more multidirectional piston home position direction.

List of numerals

1 brake shell 31 cooperates pressure face

1a cover plate 33 compression springs

Indentation section 34 thrust bearings in the 1b cover plate

2 pressure plungers, 35 thrust bearings

2a york piece 36 thrust bearings

3 cladding plates, 37 compression springs

4 brake strips, 38 slip clutch

39 pressure clutch in 5 friction coverings

6 brake disc 40a grooves

The control lever 40b groove of 7 checking cylinders

10 adjust element 41 clamp rings

The 11 41b grooves that are threaded

12 pressure faces, 42 pins

12a cooperates pressure face 43 compression springs

13 clamping levers, 50 sleeves

14 swing links (Kulisse), 51 inserts

15 flat bearings, 52 dihedral rings

21 screw members (nut), 53 nuts

21a screw member 54 threaded journal

21b screw member 59 pressure elements

22 screw members (leading screw), 60 pressure elements

23 spirals connect the 60a pressure side

24 cylindrical portion sections, 61 hinges

25 holes, 62 center lines

27 square toes, 63 hinge bodies

281. terminal backstop 66 and the fixing bearing of shell

292. terminal backstop 67a rolling element

30 pressure side 67b rolling elements

67c backstop 134 spigot edges

68 raceways, 137 pressure springs

69 raceways, 138 overrunning clutchs

70 depressions, 139 torque clutch

71 radius, 140 gears

73 delimit projection 141 tooth portions

110 adjust element 142 scarfing devices

111 be threaded 150 terminal backstops, tooth sides

112 pressure sides, 151 terminal backstops, tooth side

113 housings, 160 spherical journals

121 screw members, 161 spherical mounts

The housing of 121a screw section section 164 overrunning clutchs

122 screw members, 165 locking bodies

122a screw section section 166 rolling elements

Extension 167 friction rings of 122b side direction

123 spirals connect 168 guard rings

124 cylindrical portion section A lever free ends

125 sleeves, overcoat B zone

126 sleeves, interior cover D rotation axis

127 polygonal guiding device F impacting forces

128 caliper component L air gaps

129 R of tooth portion chamfering radius

130 spheroid S1, first axial clearance

130a ball bearing retainer S2 second axial clearance

131 thrust-bearing S3 axial clearances, thread pitch

132 groove V wearing and tearing

133 sliding bearing W reduction amounts

Claims

1. wheel drag that has integrated regulating device, it comprises: a guiding and to the pressure plunger (2) of brake strip (4) work in brake shell (1), a hold down gag that is used to handle pressure plunger (2), and, the adjustment element (10 in line of force that is arranged between inner hold down gag of brake shell (1) and the pressure plunger (2); 110), this adjustment element is threaded with pressure plunger (2), it is characterized in that, described hold down gag has a deflectable clamping lever (13), this clamping lever is on one side with respect to brake shell (1) and another side supports towards the direction of pressure plunger (2), and, being provided with the pressure transfer device that is provided with in the line of force between clamping lever (13) and pressure plunger (2), this pressure transfer device comprises one first pressure elements (60; 122) and one second pressure elements (59; 133), described first pressure elements constitutes with respect to the rotatable motion of clamping lever (13) ground and has a pressure side (60a), and second pressure elements is with respect to first pressure elements (60; 122) rotatable and have one and cooperate pressure side (12a).

2. wheel drag as claimed in claim 1 is characterized in that, described second pressure elements (59; 133) adjusting element (11; 110) go up moulding.

3. wheel drag as claimed in claim 1 or 2 is characterized in that, described pressure elements (60; 122) pressure side is supported on pressure elements (59 by a sliding bearing (133); 133) on the cooperation pressure side.

4. wheel drag as claimed in claim 3 is characterized in that, as sliding bearing, is provided with a flat pad (133).

5. wheel drag as claimed in claim 4 is characterized in that, described pad (133) is a pad with holes, and at pressure elements (60; 122) a spigot edge (134) is gone up centering.

6. as each described wheel drag in the above-mentioned claim, it is characterized in that described pressure plunger (2) is a double-plunger, two single plunger of this double-plunger interconnect by a york piece (2a), with adjustment element (10; Being threaded 110) is positioned at the center of this york piece.

7. as stating each described wheel drag in the claim, it is characterized in that described adjustment element (110) is provided with a tooth portion (129).

8. wheel drag as claimed in claim 7 is characterized in that, a described tooth portion (129) and tooth portion (a 141) engagement at the gear (140) of adjusting the setting of element (110) next door.

9. wheel drag as claimed in claim 8 is characterized in that, described gear (140) is provided with scarfing device (142), is used to adjust resetting of element (110).

10. wheel drag as claimed in claim 8 is characterized in that, described gear (140) is rotatably installed on the extension (122b) of a side direction of first pressure elements (122).