CN203548651U - Disk brake for truck - Google Patents

Disk brake for truck Download PDF

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Publication number
CN203548651U
CN203548651U CN201320456195.1U CN201320456195U CN203548651U CN 203548651 U CN203548651 U CN 203548651U CN 201320456195 U CN201320456195 U CN 201320456195U CN 203548651 U CN203548651 U CN 203548651U
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CN
China
Prior art keywords
brake
distance
disk type
lining
type braker
Prior art date
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Expired - Lifetime
Application number
CN201320456195.1U
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Chinese (zh)
Inventor
约翰·鲍姆加特纳
亚历山大·韦特
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Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/04—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by moving discs or pads away from one another against radial walls of drums or cylinders
    • F16D55/06—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by moving discs or pads away from one another against radial walls of drums or cylinders without self-tightening action
    • F16D55/10—Brakes actuated by a fluid-pressure device arranged in or on the brake
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N3/00—Arrangements or adaptations of other passenger fittings, not otherwise provided for
    • B60N3/10—Arrangements or adaptations of other passenger fittings, not otherwise provided for of receptacles for food or beverages, e.g. refrigerated
    • B60N3/105—Arrangements or adaptations of other passenger fittings, not otherwise provided for of receptacles for food or beverages, e.g. refrigerated for receptables of different size or shape
    • B60N3/108—Arrangements or adaptations of other passenger fittings, not otherwise provided for of receptacles for food or beverages, e.g. refrigerated for receptables of different size or shape with resilient holding elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
    • B60R3/00—Arrangements of steps or ladders facilitating access to or on the vehicle, e.g. running-boards
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
    • B60R7/00—Stowing or holding appliances inside vehicle primarily intended for personal property smaller than suit-cases, e.g. travelling articles, or maps
    • B60R7/04—Stowing or holding appliances inside vehicle primarily intended for personal property smaller than suit-cases, e.g. travelling articles, or maps in driver or passenger space, e.g. using racks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F16D65/183—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes with force-transmitting members arranged side by side acting on a spot type force-applying member
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C2301/00—Machine characteristics, parts or accessories not otherwise provided for
    • E01C2301/30—Cabin details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/14—Mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/28—Cams; Levers with cams

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)

Abstract

A disk brake for a truck comprises a brake caliper which is fixed onto a brake support and lapped with a brake disk. A compression device is arranged in the brake caliper and provided with a rotatable brake rod on a bridge part, two parallelly and separately positioned adjustable punches are arranged in the brake rod and contact with a lining supporting plate of a compression side brake lining, the lining supporting plate longitudinally extends and is in mirror symmetry with a transverse axis, the brake lining is positioned in a lining shaft defined by corners of the brake support if a reaction side of the brake lining is abutted to the back of the brake caliper, and the brake lining is pressed towards the brake disk at a brake position from two sides. According to the design, the plane gravity of half of the lining supporting plate is smaller than the distance between the center action point of each punch and the transverse axis, and/or the center action point of each punch is smaller than the radial distance between the plane gravity to the central axis of the brake disk, and/or force vector generated by extrusion force of the inlet side punch in the brake process is smaller than the distance between force vector generated by outlet side extrusion force and the free edge of each corner of the outlet side brake support.

Description

Disk type braker for load-carrying vehicle
Technical field
The utility model relates to a kind of disk type braker for load-carrying vehicle.
Background technique
This disk type braker is fully known.For example can consult DE 94 22 342 U1 that disclose this disk type braker.
This can have large-area brake lining with disk type braker pneumatic or electromechanical means operation, to reach long as far as possible working life.
Yet, along with the use of this large size brake lining, caused pressure distribution to the problem of wearing and tearing on inhomogeneous rubbing surface.
In only thering is the disk type braker of drift (Druckstempel), in order to avoid or reduce the excessive wear of friction plate liner in pressure area, i.e. so-called hollow wearing and tearing, liner support plate is designed to solid, namely very thick.Because the stroke demand of the break that this hollow wearing and tearing need to promote, causes sending stronger noise in addition.
In this disk type braker, improved pressure distribution, be provided with two parallel and be spaced apart from each other and arrange drifts in this disk type braker, making not to need liner support plate to be designed to solid.
Yet, if diametrically to the effect of the power of drift excessive or too small or in tangent direction two drifts spacing excessive or too small, also may in this disk type braker, occur the unequal wearing and tearing of brake lining.
In addition, there is such danger, that is, due to brake lining on brake holder bight along the circumferencial direction of brake puck or the bearing height of sense of rotation is too low that corresponding brake lining is radially screwed out.This consequence causing is, brake calipers is rotating in the radial direction by the frictional force acting on the compressive plane of the brake calipers back side, and and then make this seal face in the uneven position of brake disc rubbing surface.Cause thus different compression conditions and wearing and tearing unequal and that totally increase.
Another problem is moved and is caused by so-called dynamic stress.At this, in the situation that steering force is larger, being accompanied by, brake calipers distortion is larger, power at the point of action at the brake calipers back side because brake calipers is expanded and radially outward portion moves unevenly.Therefore the danger that, exists radial skew wearing and tearing and brake lining to screw out.
Model utility content
The purpose of this utility model is, improves so such disk type braker, by realizing on the whole rubbing surface of two brake lining two brake lining friction stress therefore increasing the service life uniformly all the time.
This purpose is by realizing according to disk type braker of the present utility model, wherein, this disk type braker has in the brake holder of the vehicle side of being fixed on, the brake calipers of overlap joint brake disc, in this brake calipers, be furnished with hold down gag, this hold down gag has and acts on bridge, the brake rod of energy deflection, wherein, in this bridge, be furnished with two parallel and be spaced apart from each other and locate drifts that can regulate, this drift and longitudinal extension, liner support plate contact about the brake lining of the compression side of transversal line Mirror Symmetry, this brake lining is equally as being resisted against in reaction side the liner hoistway that brake lining on the brake calipers back side is arranged in the brake holder being limited by brake holder bight, and wherein, two brake lining are pushed to brake disc in application position by both sides, it is characterized in that, every half face center of gravity of liner support plate is put to the distance of transverse axis little than central role of affiliated drift, and/or central role point of corresponding drift is less to the radial distance of brake disc medial axis than affiliated face center of gravity, and/or the vector of force being produced by the extruding force of the drift of inlet side in braking process is less to the distance of the free edge in outlet side brake holder bight than the vector of force being produced by outlet side extruding force to the distance of the free edge in brake holder bight described in outlet side.
By this structural measure, can be optimized the distribution of pressure in brake lining, reached the minimal deformation of liner support plate and avoid screwing out from brake holder, wherein, the wearing and tearing of brake lining are uniform on whole rubbing surface.
Wearing and tearing are proportional to the friction energy transforming in unit area.This friction energy also will be determined by the product of surface pressure x friction factor x area x friction velocity certainly.Because friction velocity and friction radius increase pro rata, so be certain to change inversely surface pressure.Will consider on the other hand, friction factor reduces according to speed conventionally, and this must consider equally when determining pressure distribution.
At this, the outer diameter of brake disc friction ring and the ratio of the friction velocity between inner diameter are about 1.65:1.When medium friction velocity, the ratio of affiliated friction factor is about 1:0.75.Draw thus, power is introduced position, must be in the radial direction more towards brake puck center arrangement for reaching uniform wear feature central role position of drift is compared with the face center of gravity of affiliated half brake lining.
Because should make brake lining keep less weight, thus liner support plate to be designed light as far as possible, and therefore to be designed to thin-walled.Now, in order also to reach the pressure distribution of wanting in tangent direction, must when introducing point, selection power also must consider the different rigidity characteristic (Steifungsverhalten) with respect to fringe region in the region of liner support plate between drift.In brief, liner support plate now meets at the zone line between drift the support that both sides clamp under load on section (Streckenlast) effect, and meanwhile, the free end of liner support plate meets the support clamping in next side of interval load action.By the utility model, should select like this two distances between drift, that is, and under the condition of different distortion characteristic of considering liner end, draw with two drifts between the identical amount of deflection of mid point.
For fear of brake lining, in braking process, from brake holder, screw out, according to the utility model proposes, the vector of force being produced by the extruding force of inlet side drift in braking process is less to the distance of the free edge in outlet side brake holder bight than the vector of force being produced by outlet side extruding force to the distance of the free edge in outlet side brake holder bight.Difference between two distances is preferably at least percent 10, thereby realizes safety supports.
Other favourable design proposal of the present utility model draws in dependent claims.
Accompanying drawing explanation
Below with reference to the accompanying drawings embodiment of the present utility model is described.
Shown in figure:
Fig. 1 is in the schematic structure of disk type braker shown in the plan view of partial cross section,
Fig. 2 is at the Local map of disk type braker shown in schematic side elevation,
Fig. 3 passes disk type braker cross-sectional view according to the line III-III in Fig. 1,
Fig. 4 is the schematic diagram of the amplification of the brake rod of the disk type braker eccentric wheel track in its operating process.
Embodiment
Fig. 1 illustrates slip brake caliper disc brake, has the brake calipers 1 of overlap joint brake puck 11, and this brake calipers can remain in the brake holder 2 of vehicle side movably.
In brake holder 2, be furnished with two brake lining 8, correspondingly liner support plate 9 and the friction covering face 10 being fixed on this liner support plate, consist of, this friction covering face can press to brake disc 11 when break is operated.
For this reason, be furnished with hold down gag 3 in brake calipers 1, have two drifts 4, this drift vertically adjustable ground is supported in bridge 5, and end effect is compressing on the affiliated liner support plate of side brake lining 8.
In braking process, tappet 13 that can be pneumatic or Electromechanically operated presses to brake rod 6(Fig. 3), this brake rod is designed to eccentric wheel 15 at the other end, and this eccentric wheel is resisted against on the supporting axle 14 being supported on bridge 5 on the one hand, and be resisted against on the other hand on the eccentric wheel track 16 of brake calipers 1.
In order to compensate the space of the brake lining 8 being caused by wearing and tearing, be provided with the regulating device 7 meshing with drift 4, can compensate described space by reversing this regulating device.
In Fig. 2, can identify the brake lining 8 that is contained in the longitudinal extension of both sides in the liner hoistway of brake holder bight 12 restrictions, this brake lining is designed to the Mirror Symmetry about transversal line Q.
According to the utility model, every half face center of gravity S1 of liner support plate 9, S2 is less to the distance of transversal line Q than central role point Z of affiliated drift 4, and the profile of this drift is shown in broken lines in Fig. 2.
Alternatively or as a supplement, central role point Z of corresponding drift 4 is to the radial distance X of brake disc 11 medial axis M 5than affiliated face center of gravity S1, S2 is to the radial distance X of medial axis 6little.
In addition the vector of force F2 being produced by the extruding force of inlet side drift 4 in braking process, is less to the distance a of the free edge in this brake holder bight than the vector of force F1 being produced by outlet side extruding force to the distance b of the free edge K in outlet side brake holder bight 12.
In example, the length L of liner support plate 9 is 248mm, central role point Z of two drifts 4 distance X each other 1for 131mm, and face center of gravity S1, S2 distance X each other 2for 116.4mm.Utilize this deviation of about 15 millimeters can reach for the brake-lining size of considering minimum generally amount of deflection.
Face center of gravity S1, the distance X between the supporting member A in the liner hoistway of S2 and brake holder 2 7it is 50 millimeters.Two center of gravity S1, the connection straight line of S2 is that best line of action of force is shown in theory, and the distance X between the medial axis M of brake disc 11 6for 163mm, and the connection straight line of two central role point Z and the distance X between the M of medial axis 5for 161mm, wherein, the Measurement Allowance of this line of action of force is between 159 to 162mm.
Thus, according to mean value, line of action of force is positioned at two face center of gravity S1, and the connecting line following about 2 of S2, to 3mm, can carry out gratifying compensation to the impact of the friction velocity increasing in the radial direction thus under the condition of speed dependence of considering coefficient of friction of brake linings.
In example, necessary bearing height, brake holder bight 12 edge K are 71mm to the height of the supporting surface A of liner hoistway, and friction radius R is 172.6mm.
Fig. 3 illustrates the sectional view of disk type braker as lever motion principle schematic, and meanwhile, Fig. 4 is illustrated in the schematic diagram of the amplification of eccentric wheel track 16 in the process that brake rod 6 is operated.
The in the situation that at steering force, thereby large and brake calipers distortion being larger, also can cause courses of action longer, the run-on point of the joint shaft bearing of supporting axle 14 parallel deviate on its ring track moves up several 1/10th millimeters in the straight line of brake disc axis in the M side, medial axis of brake puck.Thus, cause bridge 5 and be tightened in drift 4 slight inclination wherein, thereby make the pressure side of drift 4 also with respect to brake disc rubbing surface slight inclination, exactly, pressure side inner radial is less to the distance of brake disc rubbing surface than radially outer, as shown by arrows.Thus, the radially inner effect of mobile performance to the effect of the power of drift 4.
Because now to the effect of the power at the pincers back side with bridge 5 positioned opposite due to unequal expansion and radially outward moves and the effect of the power of drift 4 is radially moved inward because run-on point shifts, so the distance based on line of force produces and acts on the torque on brake calipers 1 transverse to longitudinal axis, this torque is the effect of running counter to wish of correcting brake calipers expansion to the effect of brake calipers 1.
In order to reach this effect, design like this device of the eccentric wheel track 16 of lever bearings, that is, after overcoming space, substantially only also carry out joint shaft bearing run-on point off-straight to the motion of brake disc spin axis.In the full row stroke of break, the deviation X between this and straight line 4minimum is 0.3mm, is 0.8mm to the maximum.
It is that radially outward limits this pressure side that another kind can be avoided the compressive plane of the brake calipers back of the body and the possibility of the uneven consequence of brake disc rubbing surface.Can realize thus, uneven compressive plane is just limitedly introduced than exerting an influence the power at the brake calipers back side.
For realizing below the optimizing design scheme of disk type braker of uniform brake lining 8 wearing characters passes through, the structure characteristic with compound mode application possible in the situation that realizes, and wherein, the unit of dimensioning is millimeter.In addition, this example is to be of a size of 22.5 for wheel disc " disk type braker design.
Figure DEST_PATH_GDA0000463023060000071
Figure DEST_PATH_GDA0000463023060000081

Claims (14)

1. the disk type braker for load-carrying vehicle, have in the brake holder (2) of the vehicle side of being fixed on, the brake calipers (1) of overlap joint brake disc (11), in described brake calipers, be furnished with hold down gag (3), described hold down gag has and acts on bridge (5), the brake rod (6) of energy deflection, wherein, in described bridge (5), be furnished with two parallel and be spaced apart from each other and locate drifts (4) that can regulate, described drift and longitudinal extension, liner support plate (9) contact about the brake lining (8) of the compression side of transversal line (Q) Mirror Symmetry, described brake lining is equally as being resisted against in reaction side the liner hoistway that described brake lining (8) on described brake calipers (1) back side is arranged in the described brake holder (2) being limited by brake holder bight (12), and wherein, two described brake lining (8) are pushed to described brake disc (11) in application position by both sides, it is characterized in that, every half face center of gravity of described liner support plate (9) is less to the distance of described transverse axis (Q) than central role point (Z) of affiliated described drift (4), and/or described central role point (Z) of corresponding described drift (4) is than affiliated described center of gravity (S1, S2) little to the radial distance of described brake disc (11) medial axis, and/or the vector of force (F2) being produced by the extruding force of the drift (4) of inlet side in braking process is less to the distance (a) of the described free edge in brake holder bight described in outlet side than the vector of force (F1) being produced by outlet side extruding force to the distance (b) of the free edge (K) of brake holder bight (12) described in outlet side.
2. disk type braker according to claim 1, is characterized in that, described distance (a) is at least than described distance (b) large 10%.
3. disk type braker according to claim 1 and 2, it is characterized in that, the spacing of two described centers of gravity (S1, S2) is of a size of 22.5 at wheel disc " disk type braker in be 112 – 120mm, and the spacing of described central role point (Z) is 125 – 136mm.
4. disk type braker according to claim 3, is characterized in that, the distance (X between corresponding described center of gravity (S1, S2) and the supporting surface (A) of described brake holder (2) 7) be 45 – 52mm.
5. disk type braker according to claim 3, is characterized in that, the described free edge (K) in described brake holder bight (12) is to the tangent distance (X of the described medial axis of described brake disc (11) (M) 3) be 180 – 190mm.
6. disk type braker according to claim 4, is characterized in that, the described free edge (K) in described brake holder bight (12) is to the tangent distance (X of the described medial axis of described brake disc (11) (M) 3) be 180 – 190mm.
7. disk type braker according to claim 1 and 2, is characterized in that, the described free edge (K) in corresponding described brake holder bight (12) to the distance of described supporting surface (A) is 67 – 80mm.
8. disk type braker according to claim 6, is characterized in that, the described free edge (K) in corresponding described brake holder bight (12) to the distance of described supporting surface (A) is 67 – 80mm.
9. disk type braker according to claim 1 and 2, is characterized in that, the described supporting surface of the described brake lining (8) of reaction side has declining edge on described brake calipers (1) pincers dorsal part.
10. disk type braker according to claim 8, is characterized in that, the described supporting surface of the described brake lining (8) of reaction side has declining edge on described brake calipers (1) pincers dorsal part.
11. disk type brakers according to claim 1 and 2, is characterized in that, described center of gravity (S1, S2) is to the tangent distance (X of described medial axis (M) 6) be 158 – 165mm.
12. disk type brakers according to claim 10, is characterized in that, described center of gravity (S1, S2) is to the tangent distance (X of described medial axis (M) 6) be 158 – 165mm.
13. disk type brakers according to claim 1 and 2, is characterized in that, described central role point (Z) is to the tangent distance (X of described medial axis (M) 5) be 157 – 163mm.
14. disk type brakers according to claim 12, is characterized in that, described central role point (Z) is to the tangent distance (X of described medial axis (M) 5) be 157 – 163mm.
CN201320456195.1U 2012-10-31 2013-07-29 Disk brake for truck Expired - Lifetime CN203548651U (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012110458.1A DE102012110458A1 (en) 2012-10-31 2012-10-31 Disk brake for commercial vehicle, has swingable brake lever attached with bridge, and adjustable piston rams arranged in bridge in parallel manner and stretched along lateral axis of liner support plate
DE102012110458.1 2012-10-31

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Publication Number Publication Date
CN203548651U true CN203548651U (en) 2014-04-16

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CN201320456195.1U Expired - Lifetime CN203548651U (en) 2012-10-31 2013-07-29 Disk brake for truck

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DE (2) DE102012110458A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108071716A (en) * 2016-11-18 2018-05-25 凯尔西-海耶斯公司 For the controlled exposure guide pin of vehicle disc brake
CN116292676A (en) * 2023-02-14 2023-06-23 贝格纳电子科技(济南)有限公司 Air pressure disc brake

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CN108071716A (en) * 2016-11-18 2018-05-25 凯尔西-海耶斯公司 For the controlled exposure guide pin of vehicle disc brake
CN116292676A (en) * 2023-02-14 2023-06-23 贝格纳电子科技(济南)有限公司 Air pressure disc brake
CN116292676B (en) * 2023-02-14 2023-08-22 贝格纳电子科技(济南)有限公司 Air pressure disc brake

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