CN101504045B - Disc brake friction member assembly - Google Patents
Disc brake friction member assembly Download PDFInfo
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- CN101504045B CN101504045B CN 200910005557 CN200910005557A CN101504045B CN 101504045 B CN101504045 B CN 101504045B CN 200910005557 CN200910005557 CN 200910005557 CN 200910005557 A CN200910005557 A CN 200910005557A CN 101504045 B CN101504045 B CN 101504045B
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- member assembly
- dash receiver
- disc brake
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Abstract
A disc brake friction member assembly (1, 1A, 1B) is provided with: a torque receiving plate (17); an anchor plate (48) fixed to a rear surface of the torque receiving plate (17); a cut-and-erected portion (63) formed on the rear surface of the torque receiving plate (17) and having an abutment surface (61) along a direction orthogonal to a direction in which the brake torque is applied; and a cut-out portion (65) provided on the anchor plate (48). A friction member (5) is attached on a front side of the torque receiving member (17) and the torque receiving member (17) receives a brake torque applied to the friction member (5). The cut-and-erected portion (63) fits to the cut-out portion (48). The cut-out portion (65) receives the brake torque via the abutment surface (61).
Description
Technical field
The present invention relates to a kind of disc brake friction member assembly, it for example is used for the disk brake system of rail vehicle.
Background technique
Disk braking system comprises disc rotor, the disc brake friction member assembly that is fixed on the wheel shaft, it is set in the face of disc rotor and brake calipers, this brake calipers comprises towards and drives the break of this disc brake friction member assembly away from disc rotor ground, and is fixed to body shell.This disk brake system is owing to the sliding friction that the friction member at this disc brake friction member assembly produces when compressing disc rotor produces retarding torque.
In the disc brake friction member assembly of the disk braking system that is used for rail vehicle, this disc brake friction member assembly generally includes torque dash receiver (this also can be called pressure disk), be suitable for being pressed on friction member on the disc rotor the setting of the surface side of this torque dash receiver, and this torque dash receiver receives the retarding torque that is applied on this friction member; And anchor slab, it not only is fastened on the rear surface of described torque dash receiver, and is connected to the anchor block on body side, with the transmission of torque that is used for described torque dash receiver is received to this anchor block.(for example, with reference to JP-Y2-2564497.)
In addition, as a kind of the torque dash receiver is fastened to fastening structure on the anchor slab, known a kind of structure wherein is inserted into the pressure fitted pin torque dash receiver and anchor slab in the two, in order to interconnect each plate in the mode that can transmit retarding torque between it.
Yet, because the pressure fitted pin that connects anchor slab and torque dash receiver is along its whole circumference drive fit and without any loosening (play) in each plate, not only transmitting load on disc rotor tangential of retarding torque when applying when braking, and the load that makes progress with the footpath at disc rotor that the thermal distortion of each plate produces, all be applied on the pressure fitted pin, and in this pressure fitted pin, metal fatigue take place easily.Thus, in order to prevent because the destruction of the pressure fitted pin that causes of metal fatigue and can not transmit the major accident of braking force, must implement maintenance and inspection work continually, replacing friction member assembly in the stage in early days, thereby caused increasing the problem of quantity of the enforcement number of times of maintenance and the work of inspection.
In addition, in rail vehicle, because disc brake friction member assembly is tending towards becoming dimensionally very big, the split type disc brake friction member assembly that is made of a plurality of friction member assemblies that the circumferencial direction series connection at disc rotor arranges has been proposed also.
Each friction member assembly all comprises the torque dash receiver, and the friction member that is suitable for being pressed on the disc rotor is arranged on the front surface side of this torque dash receiver, and this torque dash receiver receives the retarding torque that is applied to friction member; And the anchor slab that is fastened to the rear surface of torque dash receiver.
In the friction member assembly of series connection alignment, the anchor slab that is positioned at the disc brake friction member assembly on the downstream side of sense of rotation of disc rotor is adjacent with the anchor slab that is fixed to vehicle body, and the retarding torque that is applied to the friction member assembly on the upstream side of the sense of rotation that is positioned at disc rotor thus is passed on the anchor block via being close to this friction member assembly in the downstream side.
A plurality of friction member assemblies series connection therein is arranged in traditional split type disk type braker on the circumferencial direction of disc rotor, because the friction member assembly that closes on each other under the state that series connection arranges is adjacent to each other at its place, end, the edge of while anchor slab and the end part aligning of torque dash receiver, according to tolerance of size or the foozle of each friction member assembly, bring torque dash receiver worry with regard to being adjacent to each other before its anchor slab is adjacent to each other that will cause each assembly.When this took place, the retarding torque that can cause the friction member assembly on the upstream side that is input to the sense of rotation that is positioned at disc rotor was passed on the torque dash receiver of friction component of the close upstream side friction member assembly on the downstream side of the sense of rotation that is positioned at disc rotor.
The result, the retarding torque that is received by the friction member assembly on the upstream side of the sense of rotation that is positioned at disc rotor is imported on the torque dash receiver of the friction member assembly on the downstream side of the sense of rotation that is positioned at disc rotor, as external torque, thus, excessive load is applied on the connection set between torque dash receiver and the anchor slab, and the serviceability that has caused causing friction member assembly reduces or constitutes the rivet of connection set or the worry of the ruined significant problem of weld seam.
Summary of the invention
One or more embodiment of the present invention provides a kind of disc brake friction member assembly, wherein in the anastomosis part of transmitting retarding torque, be difficult to take place metal fatigue, therefore can reduce for the maintenance that detects metal fatigue and the frequency of inspection, to increase operating characteristics, and therefore this disc brake friction member assembly not only can increase assembly properties by the quantity that reduces part, but also can realize reducing production costs.
In addition, one or more embodiment of the present invention provides a kind of disc brake friction member assembly, it comprises a plurality of friction member assemblies on the circumferencial direction that is arranged on disc rotor of connecting, wherein the retarding torque that receives of the friction member assembly on the upstream side of the sense of rotation by being positioned at disc rotor is not imported into the torque dash receiver of the friction member assembly on the downstream side of the sense of rotation that is positioned at disc rotor, therefore, reduced the serviceability of this friction member assembly owing to excessive load or such as the destruction of the connection set of rivet.
According to one or more embodiment of the present invention, disc brake friction member assembly has: the torque dash receiver, and wherein friction member is connected on the front side of this torque receiving element, and this torque receiving element receives the retarding torque that is applied on this friction member; Anchor slab, it is fixed to the rear surface of torque dash receiver and is connected on the anchor block of body side; Cutting and vertical part, it is formed on the rear surface of torque dash receiver, and has abutment surface along the direction with the direction quadrature that applies retarding torque; And being arranged on cut out portion on the anchor slab, wherein said cutting and vertical portion branch are coupled to this cut out portion, so that this cut out portion receives retarding torque via abutment surface.
In this disc brake friction member assembly, this disc brake friction member assembly can be divided into two disc brake friction member assemblies that align in the direction that applies retarding torque.
In above-mentioned disc brake friction member assembly, by at the cutting on the torque dash receiver and vertically part and the projection that cooperates between the cut out portion on the anchor slab and groove, retarding torque is delivered to anchor slab from the torque dash receiver.
In described cutting and this projection and groove of vertically cooperating between part and the cut out portion, make this cutting and vertically part upwards fit loosely in the described cut out portion in the footpath with the disc rotor of the direction right angle intersection of transmission retarding torque.Thus, can avoid because the applying of the radial load that the thermal distortion of projection and groove fit part is produced between each plate.
The result, when with by the pressure fitted pin conventional situation that each plate connects together is compared, reduced to be applied to the load of projection and groove fit part, this projection and groove fit partly are the anastomosis parts of transmitting for retarding torque, make thus to be difficult to produce metal fatigue in this projection and groove fit part.
As a result, can reduce to detect the number of the enforcement number of times of the maintenance of metal fatigue and the work of inspection, in order to increase the operating characteristics of this disc brake friction member assembly.
In addition, because this cutting and the vertical part that are arranged on the torque dash receiver are formed on the torque dash receiver, so compare with the traditional disc brake friction member assembly that uses independent pressure fitted pin, not only can increase assembly properties by the number that reduces included constituent elements, and can realize reducing cost of production.
In addition, according to one or more embodiments of the present invention, this disc brake friction member assembly has a plurality of friction member assemblies on the circumferencial direction that is arranged on disc rotor of connecting.Each friction member assembly all has: the torque dash receiver that is used for receiving the retarding torque that is applied on the friction member; And the anchor slab that is fixed to the rear surface of this torque dash receiver.This anchor slab is adjacent with the anchor block that is fixed to vehicle body, in order to retarding torque is delivered to this anchor block.End by the specific torque dash receiver is the end of outstanding anchor slab more, and series connection setting is adjacent to each other with the friction member assembly that closes on each other.
In above-mentioned disc brake friction member assembly, because the place, end at the anchor slab that connects in the outstanding more such mode in the end of specific torque dash receiver, series connection setting is adjacent to each other with the friction member assembly that closes on each other, simultaneously the torque dash receiver is from separated from one another, and the retarding torque that is applied on the torque dash receiver of the friction member assembly on the upstream side of the sense of rotation that is positioned at disc rotor is delivered on the anchor slab of the friction member assembly that closes on it on the downstream side by the anchor slab from the upstream side friction member assembly.Therefore, this retarding torque is not passed on the torque dash receiver of downstream side friction member assembly.
The result, in series connection is arranged on each friction member assembly on the circumferencial direction of disc rotor, the retarding torque that is received by friction member assembly on the upstream side of the sense of rotation that is arranged in disc rotor is not imported into the torque dash receiver of the friction member assembly on the downstream side of the sense of rotation that is positioned at disc rotor, can avoid reducing owing to excessive load the problem of serviceability or connection set inefficacy thus, otherwise this problem will produce in the friction member assembly of downstream side.
Description of drawings
Fig. 1 is the front elevation according to the disc brake friction member assembly of first illustrative examples of the present invention.
Fig. 2 is the rear view of disc brake friction member assembly shown in Figure 1.
Fig. 3 is the schematic representation that the shown direction of the arrow A in Fig. 2 is watched disc brake friction member assembly.
Fig. 4 is the perspective exploded view of the disc brake friction member assembly shown in Fig. 2.
Fig. 5 (a) is the explanatory schematic representation that leaf spring shown in Figure 4 is connected to the step of bush assembly to Fig. 5 (c).
Fig. 6 wherein removes torque dash receiver and anchor slab from this disc brake friction member assembly, in order to expose reception from the rear view of the disc brake friction member assembly of the connecting plate of the pressure of each bush assembly.
Fig. 7 is the sectional view along the line B-B intercepting of Fig. 6.
Fig. 8 is the sectional view along the line C-C intercepting of Fig. 6.
Fig. 9 is the sectional view along the line D-D intercepting of Fig. 1.
Figure 10 is the sectional view along the line E-E intercepting of Fig. 2.
Figure 11 is the front elevation according to the disc brake friction member assembly of second illustrative examples of the present invention.
Figure 12 is the schematic representation of the direction shown in the arrow 12 in Figure 11 when watching.
Figure 13 is the schematic representation when the direction shown in the arrow 13 is watched.
Figure 14 is the front elevation according to the disc brake friction member assembly of the 3rd illustrative examples of the present invention.
Figure 15 is the rear view at the disc brake friction member assembly shown in Figure 14.
Figure 16 is the schematic representation when the direction shown in the arrow 16 of Figure 15 is watched.
Figure 17 is the sectional view along the line 17-17 intercepting of Figure 14.
Figure 18 show friction member assembly shown in Figure 15 one of them anchor slab and the perspective view of the state that is removed of torque dash receiver.
Figure 19 is the sectional view along the line 19-19 intercepting of Figure 15.
Figure 20 is the sectional view along the line 20-20 intercepting of Figure 15.
The explanation of reference number
1 ... disc brake friction member assembly
1A, 1B ... disc brake friction member assembly
3 ... friction member
4 ... backing plate
5 ... bush assembly
7 ... the transmission of torque ring
11 ... pilot hole
12 ... pilot hole
15 ... leaf spring
17 ... the torque dash receiver
21 ... the rear surface adjacent part
22 ... the plate adjacent part
24,25 ... connecting plate
27 ... the coupling shaft part
28 ... fastening piece
31 ... matching hole
32 ... rotation restriction depression
33 ... recess
35 ... local opening
37 ... otch
43 ... rotation restriction projection
48 ... anchor slab
61 ... adjacent part
63 ... cutting and vertical part
65 ... cut-out
101 ... disc brake friction member assembly
103A, 103B ... friction member assembly
105A, 105B ... friction member
107A, 107B ... the torque dash receiver
109A, 109B ... anchor slab
111 ... spot welding
113 ... the rivet piece
121 ... disc brake friction member assembly
123A, 123B ... friction member assembly
125 ... friction member
127A, 127B ... the torque dash receiver
129A, 129B ... anchor slab
131 ... rivet
141 ... make-ready
142 ... spacer assembly
145A, 145B ... guide plate
147 ... rivet
151 ... the liner mounting hole
153,154 ... connecting plate
156 ... the spherical part that dome ground rises
157 ... locking hole
158 ... locking ratchet
Specific embodiment
Hereinafter, with the illustrative examples that is described in detail with reference to the attached drawings according to disc brake friction member assembly of the present invention.
[first illustrative examples]
Fig. 1 is the front elevation according to the disc brake friction member assembly of first illustrative examples of the present invention.Fig. 2 is the rear view of disc brake friction member assembly shown in Figure 1.Fig. 3 is the schematic representation that the shown direction of the arrow A in Fig. 2 is watched the result of disc brake friction member assembly.Fig. 4 is the perspective exploded view of the disc brake friction member assembly shown in Fig. 2.Fig. 5 (a) is the explanatory schematic representation that leaf spring shown in Figure 4 is connected to the step of bush assembly to Fig. 5 (c).Fig. 6 wherein removes torque dash receiver and anchor slab from this disc brake friction member assembly, in order to be exposed to reception from the rear view of the disc brake friction member assembly of the connecting plate of the pressure of each bush assembly.Fig. 7 is the sectional view along the line B-B intercepting of Fig. 6.Fig. 8 is the sectional view along the line C-C intercepting of Fig. 6.Fig. 9 is the sectional view along the line D-D intercepting of Fig. 1.Figure 10 is the sectional view along the line E-E intercepting of Fig. 2.
As shown in Figure 1, disc brake friction member assembly is divided into two disc brake friction member assembly 1A and 1B, these two disc brake friction member assembly 1A and 1B are arranged in such a way, in order to applying on the direction of retarding torque (on the tangent direction at disc rotor, i.e. direction shown in the arrow P among Fig. 1) alignment.
Because these two disc brake friction member assembly 1A and 1B have identical construction like this, so will do detailed description to the each several part structure of disc brake friction member assembly 1A.
Disc brake friction member assembly 1A comprises the unshowned guide plate 11 with a plurality of bush assemblies 5, and wherein backing plate (backing plate) 4 is fastened on the rear surface of the friction member 3 that is pressed on disc rotor; Transmission of torque ring 7, each forms the roughly disc-shape with external shape littler than backing plate 4, and is connected respectively to the center of backing plate 4; And 5 pilot holes 11, wherein the external peripheral surface 7a of transmission of torque ring 7 cooperates by this way in order to rotate in this pilot hole 11, and this pilot hole 11 is suitable for receiving the retarding torque that is applied to bush assembly 5 via transmission of torque ring 7; Leaf spring 15, its each have the external shape bigger than pilot hole 11, and be placed on the top of pilot hole 11 by this way in order to be connected to bush assembly 5, thus bush assembly 5 and transmission of torque ring 7 are remained to guide plate 12, so that rotation thereon; Torque dash receiver 17, its support guide plate 12 is in order to receive the retarding torque that is applied to guide plate; And two kinds of connecting plates 24 and 25, its each comprise with a plurality of rear surfaces adjacent parts (rear surface is in abutting connection with curvature portion) 21 of the rear surface adjacency of a plurality of bush assemblies 5 and with the single plate adjacent part 22 of torque dash receiver 17 adjacency, and be suitable between bush assembly 5 and torque dash receiver 17, transmitting pressure.
Under this embodiment's situation, as Fig. 4 and shown in Figure 7, transmission of torque ring 7 forms its diameter less than the disc-shape of the diameter of backing plate 4, and is formed on this backing plate.
As shown in Figure 7, the external peripheral surface 7a of transmission of torque ring 7 forms with the inner circumferential surface of pilot hole 11 and is a dome curved surface that contacts (convexly curved surface).By be engaged in the transmission of torque ring 7 in the pilot hole 11 at the curved surface place, spacer assembly 5 is supported in the pilot hole 11 by this way, so that the direction shown in the arrow X in Fig. 7 is rotated (swing).Follow in the fluctuation that produces in the disc rotor in order to keep for the constant contact area for friction component 3, this rotation behavior becomes necessary.
In addition, to 5 (c) and shown in Figure 8, coupling shaft part 27 and fastening piece 28 are formed on the rear surface of transmission of torque ring 7 (with the surperficial facing surfaces towards bush assembly 5) as Fig. 5 (a).Coupling shaft part 27 forms projection and becomes its diameter less than the angular pole (angular rod) of the diameter of transmission of torque ring 7, and the each several part that fastening piece 28 forms the distal side (with towards the relative side of a side of transmission of torque ring 7) from coupling shaft part 27 radially extends.
At this fastening piece 28 and in the face of the space between the transmission of torque ring 7 of this fastening piece 28 has constituted groove, the circumference edge portion of the matching hole 31 in the leaf spring 15 that will be described below embeds (barge) in this groove by fastening piece 28 is set like this.
To 5 (c) and shown in Figure 8, on transmission of torque ring 7, rotation limits depression 32 free spaces that are formed on the periphery that is arranged in coupling shaft part 27 as Fig. 5 (a).
Under the situation of present embodiment, rotation restriction depression 32 is circular matching holes.
Coupling shaft part 27 rotatably is engaged in the circular matching hole 31 that is formed in the leaf spring 15.
Shown in Fig. 5 (a), leaf spring 15 has recess 33, and this recess 33 is connected to circumference edge portion 31 constantly with as its part, in order to make fastening piece 28 to pass through at this.
Shown in Fig. 5 (a), by recess 33 is set like this, this recess 33 is located by this way so that consistent with the position (location) of fastening piece 28, so that coupling shaft part 27 and fastening piece 28 can pass through matching hole 31, to realize the state shown in Fig. 5 (b) thus, and shown in Fig. 5 (c), leaf spring rotates in the direction shown in the arrow Y, in order between spacer assembly 5 and leaf spring 15, produce relative rotation, thus, the circumference edge portion of matching hole 31 is embedded in the groove shape part between fastening piece 28 and the transmission of torque ring 7 relative with this fastening piece 28, and the result prevents that wherein leaf spring 15 is from the state of coupling shaft part 27 displacements.
Shown in Fig. 5 (c), when leaf spring 15 and coupling shaft part 27 have relatively been rotated about 90 °, in order to produce when preventing leaf spring 15 from the state of coupling shaft part 27 displacements, local opening 35 (the radial groove part on inner-diameter portion whose) is formed in the leaf spring 15 by this way, so that overlapping with the rotation restriction depression 32 that is formed in the transmission of torque ring 7.
As shown in Figure 6 and Figure 7, leaf spring 15 in order to produce diastrophic excircle part 15a thus outside between circumferential section and the inner circumferential portion, and demonstrates resiliency characteristics by contacting with guide plate 12.Yet shown in Fig. 5 (a), otch 37 is arranged on four positions on the excircle part, in order on the circumferential section contact segment is divided into guide plate 12 outside.
When leaf spring 15 is placed state shown in Fig. 5 (c) from the state shown in Fig. 5 (b), shown in Fig. 5 (b), near the part of core that is positioned at the leaf spring 15 that is engaged on the coupling shaft part 27 is pressed towards guide plate 12 thrusters, so that leaf spring 15 resiliently deformables, and when this leaf spring 15 is with respect to coupling shaft part 27 half-twists in this state, caused the state shown in Fig. 5 (c).
The guide plate 12 of present embodiment has 5 pilot holes 11.When the transmission of torque ring 7 of bush assembly 5 is engaged in respectively in the pilot hole 11, and be engaged in leaf spring 15 on the coupling shaft part 27 of transmission of torque ring 7 projections of each bush assembly 5 afterwards and be placed in skew shown in Fig. 5 (c) when preventing state, finished the combine part assembly 41. of (Fig. 6, the state that link 24,25 is removed) of wherein these 5 bush assemblies and guide plate 12
Manufacture method as the disc brake friction member assembly 1 of present embodiment, adopt a kind of like this manufacture method, it comprises part assembly 41 is incorporated into step in the production line, this part assembly 41 is to finish so that these five bush assemblies 5 combine with guide plate 12 in advance by setting up bush assembly 5 in all pilot holes 11 in guide plate 12 in the above described manner, then as shown in Figure 6, from the rear surface side of guide plate 12 each connecting plate 24,25 is set up on the described part assembly 41, and torque dash receiver 17 is fastened to guide plate 12.
As shown in Figure 6, make connecting plate 24 so be fastened to two bush assemblies 5, these two bush assemblies 5 remain on the guide plate 12 by this way in order to transmit pressure.Rear surface adjacent part 21 is arranged in such a way each the end place at connecting plate 24, so as with the rear surface adjacency of each bush assembly 5.In addition, single plate adjacent part 22 is arranged in such a way the neutral position between two rear surface adjacent parts 21, so as with torque dash receiver 17 adjacency.
As shown in Figure 8, adjacent by making towards the center at the top of the curved surface part 21a of bush assembly 5 lateral processes and coupling shaft part 27, rear surface adjacent part 21 has been guaranteed the pressure transmission between bush assembly 5 and connecting plate 24, and need not sacrifice the rotational characteristic by the bush assembly 5 shown in the arrow X among Fig. 7.
As shown in Figure 9, adjacent towards curved surface part 22a and the torque dash receiver 17 of torque dash receiver 17 lateral processes by making, via the rotatable adjacency of connecting plate 24 with torque dash receiver 17, plate adjacent part 22 has been guaranteed the pressure transmission between torque dash receiver 17 and connecting plate 24.
As shown in Figure 6, make connecting plate 25 to transmit fastening three bush assemblies 5 of mode of pressure, these three bush assemblies 5 are maintained on the guide plate 12.Rear surface adjacent part 21 is arranged on the distal side of arm shape part, and this arm shape part is extended in three directions from the center of connecting plate 25 by this way, with the rear surface adjacency of each bush assembly 5.In addition, single plate adjacent part 22 is arranged in such a way in order to be positioned at the middle part of connecting plate 25, and plate adjacent part 22 manufactures and torque dash receiver 17 adjacency.
The structure of rear surface adjacent part 21 and plate adjacent part 22 is identical with the structure of the rear surface adjacent part 21 of above-described connecting plate 24 and plate adjacent part 22.
As shown in Figure 7 and Figure 8, a pair of rotation restriction projection (rotation limit flexion ratchet) 43 is arranged on each back adjacent part, is used for limiting the leaf spring 15 of stack each other and the rotation of transmission of torque ring 7.
By being bent to form the protrusion on rear surface adjacent part 21 by this way in order to extend from its both sides, and the limit rotation projection 43 that causes being arranged on each connecting plate 24,25 is locking ratchet, and the rotation that will form like this restriction projection 43 manufactures in the local opening that overlaps each other 35 and rotation restriction depression 32 that is engaged in shown in Fig. 5 (c), so that the rotation of rotary liner assembly 5 and leaf spring 15.
As shown in Figure 5, torque dash receiver 7 is connected to the rear surface of guide plate 12 in this state, so that connecting plate 24,25 is arranged on each bush assembly 5 that remains on the connecting plate 12.
As shown in Figure 4, riveted joint through hole 46 is formed on the excircle part of guide plate 12 and torque dash receiver 17 with suitable spacing.Guide plate 12 and torque dash receiver 17 partly overlap each other along its excircle, and are securely connected and are fixed to each other by the rivet 47 that passes through hole 46 then.
Namely, in the situation of present embodiment, the friction member 3 that 5 form setting is set with bush assembly is via guide plate 12 and connecting plate 24,25 and be connected to torque dash receiver 17, and makes the retarding torque that is applied to this friction member 3 be passed to torque dash receiver 17 via guide plate 12.
As shown in Figure 4, in the situation of present embodiment, treat torque dash receiver 17 with the form of anchor slab spare 50, wherein anchor slab 48 is fixed to torque dash receiver 17 by rivet 49, so that this anchor slab 48 is combined into one with this torque dash receiver 17.
In the disk braking system on vehicle side, anchor slab 48 is fixed to anchor block (a kind of friction member connection set), this anchor block by break drive with towards or move away from disc rotor.
As Fig. 2 and shown in Figure 4, in disc brake friction member assembly 1A, the 1B of present embodiment, be formed with cutting and vertical part 63 in the rear surface of torque dash receiver 17, this cutting and vertical part 63 have abutment surface 61 along the direction with the direction right angle intersection that applies retarding torque.
This cutting and vertical part 63 in the step of the various piece that pushes torque dash receiver 17 forms suddenly.
In addition, cut-out 65 is formed in the anchor slab 48 that is riveted to torque dash receiver 17, therefore cutting and vertically part 63 be engaged in this cut-out 65, the retarding torque that receives by the torque dash receiver is via this cutting and vertically part 61 and 65 absorptions of cut part thus.
As shown in Figure 4, cut-out 65 is arranged to more smaller than the span between the relative abutment surface 61,61 of cutting and vertical part 63 along the A/F W of the direction that applies retarding torque, so that the cooperation of the cutting in cut-out 65 and vertical part 63 becomes very tight, so that interference fit (drive fit) to be provided.Relative therewith, cut-out 65 is configured to greater than excision and the vertical corresponding length L 2 of part 63 along the length L 1 with the direction of the direction right angle intersection that applies retarding torque, so as should excision and vertically part 63 loose fits in this cut-out 65.
By make on torque dash receiver 17 cutting and vertically part 63 be engaged in the cut-out 65 in the anchor slab 48, torque dash receiver 17 and anchor slab 48 are incorporated in the anchor slab assembly 50, and after this, clamp the rivet 49 that passes the riveted joint through hole.
As shown in Figure 9, torque dash receiver 17 is fixed in the state that the manufacturing of guide plate 12 finishes therein, each connecting plate 24,25 plate adjacent part 22 are freely to rotate the abutment of such mode and torque dash receiver 17, thus, be delivered to the pressure of torque dash receiver 17 via the break of unshowned disk brake system, be utilized plate adjacent part 22 and rear surface adjacent part 21 and be delivered to each bush assembly 5.In addition, utilize rear surface adjacent part 21 and plate adjacent part 22, the counter-force of the pressure that will produce when friction member 3 compresses disc rotor is delivered to torque dash receiver 17 from bush assembly 5, and is received by torque dash receiver 17.
On the other hand, when applying braking, the retarding torque that is applied to bush assembly 5 from disc rotor is delivered to transmission of torque ring 7 by the external peripheral surface 7a from the transmission of torque ring 7 that combines with this bush assembly 5 and is engaged in wherein guide plate 12, and after this, the retarding torque of transmitting like this is passed to the torque dash receiver 17 that is fixed in guide plate 12.In addition, so the retarding torque of transmitting is then via in cutting and the vertically projection between part 63 and the cut-out 65 and cooperating of groove and be delivered to anchor slab 48 from torque dash receiver 17, this cutting and vertical part 63 are formed on the torque dash receiver 17, and this cut-out 65 is formed on the anchor slab 48.
As described above, in the disc brake friction member assembly 1A of present embodiment, the retarding torque system of making is via in cutting and the vertically projection between part 63 and the cut-out 65 and cooperating of groove and be delivered to anchor slab 48 from torque dash receiver 17, this cutting and vertical part 63 are on torque dash receiver 17, and this cut-out 65 is in anchor slab 48.
Since as shown in figure 10 with retarding torque direction of transfer (disc rotor tangential) with the footpath of the disc rotor of right angle intersection upwards, length L 1 is arranged to greater than length L 2, and with this cutting and vertically part 63 with projection and cooperating of groove manufacture the loose fit that the 1mm order of magnitude is provided between the cut-out 65, the radial load relevant with its thermal distortion that can avoid thus producing between each plate is applied to projection and groove fit part.
As a result, when utilizing the pressure fitted pin to be connected with tradition to compare, be applied to this projection of the anastomosis part that is configured for transmitting torque and the load on the groove fit part and reduce, make to be difficult to produce metal fatigue.
For this reason, reduce the frequency of the maintenance implemented in order to detect metal fatigue and the work of inspection, made it possible to increase the treatment characteristic of this disc brake friction member assembly thus.
In addition, make the cutting and the vertical part 63 that are arranged on the torque dash receiver 17 be formed on like this on the torque dash receiver 17, and when comparing with the traditional disc brake friction member assembly that uses independent pressure fitted pin, by reducing the number of the component parts that comprises, the manufacturing characteristic not only can be increased, and cost of production can be realized reducing.
In addition, as shown in Figure 1, because disc brake friction member assembly 1 according to the present invention adopts two-part structure, wherein it is divided into two the disc brake friction member assembly 1A and the 1B that arrange in the mode of aliging in the direction that applies retarding torque, when comparing with the traditional disc brake friction member assembly that adopts structure one or a part, retarding torque is divided into to be applied to each disc brake friction member assembly 1A, two of 1B half.This has also played the effect that reduces to be applied to the load on projection and the groove fit part, makes thus to be difficult to produce metal fatigue.
[second illustrative examples]
Figure 11 is the front elevation according to the disc brake friction member assembly of second illustrative examples of the present invention, and Figure 12 is the schematic representation the when direction shown in the arrow 12 is watched in Figure 11, and Figure 13 is the schematic representation when watching from the direction shown in the arrow 13.
Disc brake friction member assembly 101 shown in Figure 11 is used in the disk brake system for rail vehicle.This disc brake friction member assembly 101 is split type disc brake friction member assemblies, and wherein two friction member assembly 103A and 103B arrange along the circumferencial direction series connection that is fixed to the unshowned disc rotor on the axle.
Each friction member assembly 103A and 103B structurally are symmetrical.Each friction member assembly 103A and 103B comprise torque dash receiver 107A, 107B and anchor slab 109A, 109B.Friction member (friction pad) 105A, the 105B that are suitable for being pressed on the disc rotor are installed on the front surface side of torque dash receiver 107A, 107B. Torque dash receiver 107A, 107B receive the torque that is applied on friction member 105A, the 105B.Anchor slab 109A, 109B are fastened to the rear surface of each torque dash receiver 107A, 107B.
In this second illustrative examples, torque dash receiver 107A, 107B are the backing plates that is fastened to the rear surface of friction member 105A, 105B.The external shape of torque dash receiver 107A, 107B is configured to the external shape greater than friction member 105A, 105B.The outer circumferential edges of torque dash receiver 107A, 107B is compared more outstanding with friction member 105A, 105B.
By the spot welding 111 of making in six spot welding positions on each torque dash receiver, make anchor slab 109A, 109B be fastened to the rear surface of corresponding torque dash receiver 107A, 107B and integral with it.
Suppose that the direction shown in the arrow X of disc rotor in Figure 11 of friction member assembly 103A, the 103B of series connection alignment rotates, be positioned at the anchor slab 109A and anchor block 113 adjacency that are fixed to vehicle body of the friction member assembly 103A on the downstream side of sense of rotation of disc rotor, and the retarding torque that is applied to the friction member assembly 103B on the upstream side of the sense of rotation that is positioned at disc rotor is delivered to anchor block 113 via friction member assembly 103A, and this friction member assembly 103A is positioned near the upstream side friction member assembly 103B in the downstream side.
As shown in figure 13, in the disc brake friction member assembly 101 of second illustrative examples, anchor slab 109A, 109B are connected respectively to torque dash receiver 107A, 107B.Length L has further been given prominence in the edge specific torque dash receiver 107A of anchor slab 109A, 109B, the end of 107B.Therefore, friction member assembly 103A, the 103B that closes on each other under the state that series connection arranges is adjacent to each other at the place, end of anchor slab 109A, 109B, and the dash receiver of torque simultaneously 107A, 107B are from the distance of the 2L that has been separated from each other.
In addition, size L is arranged to so suitable value, even so that tolerance of size and foozle accumulation, the end of anchor slab 109A, 109B is not positioned at the more inside close position, end of specific torque dash receiver 107A, 107B yet.
In above-mentioned disc brake friction member assembly 101, because the friction member assembly 103A that closes on each other under the state that series connection arranges and 103B are at specific torque dash receiver 107A, the anchor slab 109A that the end of 107B is outstanding more, the place, end of 109B is adjacent to each other, the dash receiver of torque simultaneously 107A, 107B is from being separated from each other, so be applied to the retarding torque on the torque dash receiver 107B of the friction member assembly 103B on the upstream side of the sense of rotation of disc rotor, be passed on the anchor slab 109A of the friction member assembly 103A of close upstream side friction member assembly 103B on the downstream side, rather than be passed on the torque dash receiver 107A of downstream side friction member assembly 103A.
The result, in series connection is arranged on each friction member assembly 103A and 103B on the circumferencial direction of disc rotor, the retarding torque that receives by the friction member assembly 103B on the upstream side on the sense of rotation that is positioned at disc rotor is not imported into the friction member assembly 103A on the downstream side on the sense of rotation that is positioned at disc rotor, can avoid thus since undue load will cause in the friction member assembly 103A of downstream side such as the inefficacy of the connection set of the rivet that the torque dash receiver is fastened to anchor slab or the problem that serviceability reduces, and can increase the serviceability of disc brake friction member assembly 101.
[the 3rd illustrative examples]
Figure 14 is the front elevation according to the disc brake friction member assembly of the 3rd illustrative examples of the present invention, Figure 15 is the rear view of the disc brake friction member assembly shown in Figure 14, Figure 16 is the schematic representation of the arrow 16 represented directions from Figure 15 when watching, Figure 17 is the sectional view of the line 17-17 intercepting in Figure 14, Figure 18 shows the perspective view of the state that one of them torque dash receiver of anchor slab shown in Figure 15 and friction member assembly is removed, Figure 19 is the sectional view of the line 19-19 intercepting in Figure 15, and Figure 20 is the sectional view of the line 20-20 intercepting in Figure 15.
Disc brake friction member assembly 121 shown in Figure 14 also is two-part type disc brake friction member assembly for the disk braking system of rail vehicle, and is made up of two friction member assembly 123A that arrange along the series connection of the circumferencial direction of the unshowned disc rotor that is fixed to axle and 123B.
In addition, each friction member assembly 123A and 123B structurally are symmetrical, and comprise torque dash receiver 127A, 127B, the friction member (friction pad) 125 that is suitable for being pressed on the disc rotor is arranged on the front surface side of this torque dash receiver 127A, 127B, and this torque dash receiver 127A, 127B receive and to be applied to friction member 125 and to be fastened to torque on anchor slab 129A, the 129B of rear surface of each torque dash receiver 127A, 127B.
In the 3rd illustrative examples, utilize six rivets 131, with each anchor slab 129A, 129B is connected to and be attached to corresponding torque dash receiver 127A and 127B.
In the 3rd illustrative examples, friction member 125 is circular.As shown in figure 17, the rear surface of friction member 125 is connected to have on the similarly round-shaped backing plate 141, and friction member 125 and backing plate 141 have constituted spacer assembly 142.
On the front surface side of each torque dash receiver 127A, 127B, keep guide plate 145A, the 145B of spacer assembly 142 to be arranged in such a way, in order to be fixed on corresponding torque dash receiver 127A, the 127B with rivet 147.
Five mounting holes 151 that spacer assembly 142 is coupled to wherein are formed among each guide plate 145A, 145B.
As shown in figure 18,5 spacer assemblies 142 that are arranged among each guide plate 145A, 145B are divided into two groups, are made up of two liners for one group, and another group is made up of three liners, in order to supported by two connecting plates 153,154.
Shown in Figure 17 and 18, each connecting plate 153,154 comprises and is suitable for the spherical part 156 that the dome with the center adjacency of the backing plate 141 of each spacer assembly 142 rises and is adapted to fit in locking ratchet 158 in the locking hole 157 that is formed on from the position that the center of backing plate 141 separates.In addition, connecting plate 153,154 and in lip-deep torque dash receiver 127A, 127B adjacency has thereafter limited the displacement of connecting plate 153,154 on their thickness direction thus.
Each spacer assembly 142 that is installed on guide plate 145A, the 145B is supported by the spherical part 156 that connecting plate 153,154 dome rise, this connecting plate 153,154 and the rear surface adjacency of this spacer assembly 142.Therefore, limited this spacer assembly 142 disc rotor axially on the position, and guaranteed the swing characteristic (wobbling action on the direction shown in the arrow Y in Figure 17) of this spacer assembly 142, this fluctuation that this spacer assembly 142 is followed the disc rotor that is produced by its thermal distortion is very necessary.
In addition, by being engaged in the locking ratchet 158 in the locking hole 157, limited the rotation of spacer assembly 142 on the direction shown in the arrow Z of Figure 14.
When with the friction member assembly 103A of second illustrative examples shown in Figure 11, when 103B compares, among friction member assembly 123A, the 123B in the 3rd illustrative examples, owing to support friction member 115 in order to freely swing via guide plate 145A, 145B and connecting plate 123A, 123B by this way, even produced fluctuation owing to its thermal distortion at disc rotor, each friction member 125 also can be followed the fluctuation of such generation, so that the good contact performance of maintenance and disc rotor.Therefore, because the fluctuation of this disc rotor will not reduce braking characteristic.
In addition, similar to second illustrative examples, friction member assembly 123A in the 3rd illustrative examples, among the 123B, equally, suppose that disc rotor is at the friction member assembly 123A of series connection alignment, 123B by rotating on the direction shown in the arrow X among Figure 14 and Figure 15, be positioned at the anchor slab 129A and anchor block 113 adjacency that are fixed to vehicle body of the friction member assembly 123A on the downstream side of sense of rotation of disc rotor, and be applied to friction member assembly on the upstream side of the sense of rotation that is arranged in disc rotor (in the 3rd illustrative examples, friction member assembly 123B) retarding torque is passed to anchor block 113 via friction member assembly 123A, and this friction member assembly 123A is near the upstream side friction member assembly 123B on the downstream side.
In addition, as shown in figure 15, same under the situation of drag friction part assembly 121, the friction member assembly 123A, the 123B that close on each other in this case that arrange in series connection are adjacent to each other at the place, end of anchor slab 129A, 129B, this anchor slab 129A, 129B are being connected to torque dash receiver 127A, 127B with this state respectively, so that the further projection in end of edge specific torque dash receiver 127A, the 127B of this anchor slab 129A, 129B size L, simultaneously torque dash receiver 127A, 127B are from the distance of the 2L that has been separated from each other.
In addition, size L is arranged to a so suitable value, although so that tolerance of size and foozle accumulation, the end of anchor slab 129A, 129B does not have the end of specific torque dash receiver 127A, 127B to be positioned at further inside position yet.
The result, in the disc brake friction member assembly 121 of the 3rd illustrative examples, equally, owing to the friction member assembly 123A that closes on each other in this case series connection setting, 123B is at anchor slab 129A, the place, end of 129B is adjacent to each other, this anchor slab 129A, 129B specific torque dash receiver 127A, the end of 127B is further outstanding, the dash receiver of torque simultaneously 127A, 127B comes from separate, the retarding torque that is applied to the friction member assembly 123A on the upstream side of the sense of rotation that is positioned at disc rotor is passed to the anchor slab 129A of friction member assembly 123A, rather than being delivered to the torque dash receiver 127A of downstream side friction member assembly 123A, this friction member assembly 123A is near the upstream side friction member assembly 123B on the downstream side.
The result, in each friction member assembly 123A, 123B that the series connection of the circumferencial direction of disc rotor arranges, the retarding torque that is received by the friction member assembly 123B on the upstream side of the sense of rotation that is arranged in disc rotor is not imported into the torque dash receiver 127A of the friction member assembly 123A on the downstream side of the sense of rotation that is positioned at disc rotor.Thus, can avoid because excessive load and the serviceability that can cause in the friction member assembly 123A of downstream reduces or such as the problem of the inefficacy of the connection set that the torque dash receiver is fastened to the rivet on the anchor slab, and can increase the serviceability of this disc brake friction member assembly 121.
Claims (2)
- A disc brake friction member assembly (1,1A, 1B), it comprises:Torque dash receiver (17), wherein friction member (5) is connected the front side of this torque dash receiver (17), and this torque dash receiver (17) receives the retarding torque that is applied to this friction member (5);Anchor slab (48), it is fixed to the rear surface of described torque dash receiver (17) and is connected to anchor block on vehicle body;Cutting and vertical part (63), it is formed on the rear surface of described torque dash receiver (17), and has abutment surface (61) along the direction with the direction quadrature that applies retarding torque; AndCut out portion (65), it is arranged on the described anchor slab (48), and wherein said cutting and vertical part (63) are coupled to this cut out portion (65), so that this cut out portion (65) receives described retarding torque via described abutment surface (61),Wherein, cut out portion (65) is configured to greater than described cutting and the vertical corresponding length (L2) of part (63) along the length (L1) with the direction of the direction quadrature that applies retarding torque, and will be in cutting and vertical the cooperating to manufacture loose fit is provided of the projection between part (63) and the cut out portion (65) and groove, make the radial load relevant with its thermal distortion of avoiding generation between described torque dash receiver (17) and described anchor slab (48) be applied to projection and the groove fit part between described cutting and vertical partly (63) and described cut out portion (65).
- 2. disc brake friction member assembly as claimed in claim 1, wherein said disc brake friction member assembly (1) be divided into two disc brake friction member assemblies aliging in the direction that applies retarding torque (1A, lB).
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008027959A JP4896902B2 (en) | 2008-02-07 | 2008-02-07 | Friction material assembly for disc brake |
| JP2008027960A JP2009185947A (en) | 2008-02-07 | 2008-02-07 | Disc brake friction material assembly |
| JP2008-027960 | 2008-02-07 | ||
| JP2008027959 | 2008-02-07 | ||
| JP2008027960 | 2008-02-07 | ||
| JP2008-027959 | 2008-02-07 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101504045A CN101504045A (en) | 2009-08-12 |
| CN101504045B true CN101504045B (en) | 2013-07-17 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200910005557 Active CN101504045B (en) | 2008-02-07 | 2009-01-20 | Disc brake friction member assembly |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4896902B2 (en) |
| CN (1) | CN101504045B (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2969726B1 (en) * | 2010-12-28 | 2013-01-18 | Faiveley Transport | FLEXIBLE FRICTION PLATE AND BRAKE LINING PROVIDED WITH SUCH A PLOT |
| JP2012229788A (en) * | 2011-04-27 | 2012-11-22 | Toyota Motor Corp | Brake apparatus, friction couple for brake apparatus, and brake pad |
| JP5918610B2 (en) | 2012-04-16 | 2016-05-18 | 曙ブレーキ工業株式会社 | Friction pad assembly for disc brake |
| JP6114008B2 (en) * | 2012-11-09 | 2017-04-12 | 曙ブレーキ工業株式会社 | Friction pad assembly for disc brake |
| US20150285321A1 (en) * | 2012-11-08 | 2015-10-08 | Akebono Brake Industry Co., Ltd. | Disc brake friction pad assembly |
| JP6073650B2 (en) * | 2012-11-08 | 2017-02-01 | 曙ブレーキ工業株式会社 | Friction pad assembly for disc brake |
| DE102015109034A1 (en) * | 2015-06-09 | 2016-12-15 | Federal-Mogul Bremsbelag Gmbh | Flexible storage of friction lining elements in brake linings |
| JP6688578B2 (en) * | 2015-09-14 | 2020-04-28 | 曙ブレーキ工業株式会社 | Friction pad assembly for disc brake |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4775036A (en) * | 1985-08-13 | 1988-10-04 | Lucas Industries Public Limited Company | Friction pad assemblies and their support |
| EP0691485A1 (en) * | 1994-07-08 | 1996-01-10 | Ferodo Italiana S.p.A. | Pads for disc brakes |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0384443A (en) * | 1989-08-28 | 1991-04-10 | Matsushita Electric Works Ltd | Combustion testing set |
| JPH0458904A (en) * | 1990-06-27 | 1992-02-25 | Sony Corp | Rack contained av apparatus |
| JPH08232999A (en) * | 1995-02-28 | 1996-09-10 | Hosei Brake Kogyo Kk | Disc brake |
| GB0106357D0 (en) * | 2001-03-13 | 2001-05-02 | Federal Mogul Friction Product | Friction pad |
-
2008
- 2008-02-07 JP JP2008027959A patent/JP4896902B2/en active Active
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2009
- 2009-01-20 CN CN 200910005557 patent/CN101504045B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4775036A (en) * | 1985-08-13 | 1988-10-04 | Lucas Industries Public Limited Company | Friction pad assemblies and their support |
| EP0691485A1 (en) * | 1994-07-08 | 1996-01-10 | Ferodo Italiana S.p.A. | Pads for disc brakes |
Non-Patent Citations (1)
| Title |
|---|
| JP特开2007-162780A 2007.06.28 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101504045A (en) | 2009-08-12 |
| JP2009185946A (en) | 2009-08-20 |
| JP4896902B2 (en) | 2012-03-14 |
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