• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:

    公开号:SU1831609A3
    申请号:SU874028845
    申请日:1987-01-16
    公开日:1993-07-30
    发明作者:Khejbel Khelmut
    申请人:Lucas Ind Plc；
    IPC主号:
    专利说明:

    The invention relates to corrective type disc brakes with a floating bracket for cars.
    The aim of the invention is the creation of a disc brake of an adjustable type with a floating (movable) bracket, in which the sliding movement of the brake pads cannot deteriorate, especially as a result of corrosion. Another objective of the invention is the creation of a brake of the type described, which will retain its functional ability for a long period of time at low production costs.
    This is achieved by that. that one of the mounting plates of the friction linings is mounted in a tangential support directly on the floating bracket, and the other is directly on the piston of the hydraulic cylinder assembly and that a long sliding guides are provided between the carrier and the piston or structural member rigidly connected to him.
    This means that in accordance with the invention, the mounting plates of the friction linings do not rest directly on the support element, which is fixedly mounted on the car. Between the support element, which is fixedly mounted on the car, and the mounting plates of the friction linings, as well as the floating bracket, relative movement is provided due to the sliding guides. which are located between the floating block and the piston of the cylinder, on the one hand, and the supporting support element, on the other hand, and which can
    1831609 AZ must be protected against spray water, so the risk of corrosion is largely eliminated.
    Friction resistance does not occur with respect to the movement of the brake linings towards and away from the brake disc in the case of a variable-speed disc type brake disc according to the invention. In this way it is guaranteed that the braking torque can be completely removed when the braking action ceases, because the friction linings can freely separate from the brake disc.
    Friction forces applied to the friction linings in the peripheral direction of the brake disk can be transmitted to the supporting support element, which is stationary attached to the vehicle symmetrically to the plane of the brake disk. This increases the stability of the entire structure.
    The only processing required by the supporting support element, which is fixedly mounted on a car in the case of a brake according to the invention, is machining on a lathe. The use of expensive broaches (reamers) is not required, since the shaft of the friction linings does not need broaching.
    If a high braking torque is applied, the support element is fixedly attached to the vehicle and bends slightly. The floating bracket and the piston or structural member rigidly connected to the piston have some freedom of articulation with respect to the axis of the brake disc, so that the floating bracket as well as the piston can compensate for minor movements of the support element, and friction linings will always create pressure on the brake disc exactly at parallel planes.
    The adjustable-type floating-type disc brake is preferably constructed with two sliding guides, each on one side of the brake disc and spaced apart in a peripheral direction. The sliding guides between the support member and the floating shoe are mounted on one side of the brake disc, while the sliding guides between the support member and the piston or structural member. rigidly connected to the piston, located on the other side of the brake disc. Due to the fact that the floating bracket and the piston of the brake cylinder or a structural element rigidly connected to it have the possibility of slight ball rotation around the central axis of the piston and cylinder assembly and the possibility of moving along this axis, installation using four sliding guides on the supporting bearing an element that is fixedly attached to the car, kinematically represents the so-called three-point support, so that the floating block and piston are statically mounted under any load.
    Preferably, the floating block and piston are provided with rationally symmetrical seats for protective covers, as this makes it possible to use simple rationally symmetrical covers and it is easy to slide on these covers.
    The sliding guides are preferably made in the form of a structure consisting of guides to the fingers and grooves, while the guiding fingers are attached to a support element that is fixedly mounted on the car, and the grooves are made in a floating block or piston or a structural member rigidly connected to the piston. You can also mount the guide fingers on the last mentioned structural elements, and make the grooves in the supporting element, motionlessly connected to the car. Regardless of the design option chosen, the slideways can be sealed with respect to the spray water using covers. It is preferable to cover the covers with a protective sheet, at least on the sides facing the friction linings, which become hot. With this protection, the covers can’t get too hot
    In the case of disc brakes of the type in question, it is important that the brake pads or the floating bracket are guided by sliding movement without any interference or difficulty. This is especially true for too large gaps between the elements, which can lead to undesirable noise such as screeching when the brakes are applied.
    Therefore, in order to guarantee the normal sliding movement of the movable elements and to avoid an undesirable screech during braking, a special modification of the invention is provided with respect to the sliding guides at the rear end of the brake, which is implemented as a tongue-and-groove connection.
    Since the forces generated by the rotation of the tomosis disk during normal braking are transmitted to the driven (rear) end of the brake and then to the bearing support element, which is fixedly connected to the vehicle, the spike-groove device according to the invention has the effect that the movable elements , i.e. a floating bracket with one of the brake linings and a piston (or a structural element rigidly connected to the piston in the form of a slider together with another brake liner are guided without a gap and are tightly mounted relative to the stationary support element.
    In a preferred modification of the invention, each wedge-shaped guide pin is mounted on a piston or structural member in the form of a slider rigidly connected to it, and on a floating bracket at the rear end of the brake. Each such guide pin engages (comes into contact) with a corresponding additional groove formed in the support element or in the intermediate part rigidly connected to it and made of steel, in particular hardened steel.
    At the front end of the brake, preferably, thorn-groove devices are not used. as slide guides. Instead, cylindrical guide fingers are provided between the piston or slider rigidly connected to the piston, as well as the floating block and the support member. These guide pins are mounted on the supporting support element and come into contact (engage) with additional grooves in the piston or slider rigidly connected to it and in the floating block or intermediate part rigidly connected to the floating bracket.
    Intermediate parts provided in accordance with an embodiment of the invention in the slide rails can be made of hardened material to improve stress resistance and extend the life of the brake.
    In a preferred embodiment of the invention, springs are installed between the support member or guide fingers and the floating block, as well as a piston at the leading end of the brake. These springs bias the floating bracket or piston toward the driven end of the brake.
    Thus, all moving brake elements (floating bracket, brake linings, piston and slider) are constantly shifted towards the driven end of the brake, so that rattling and screeching are eliminated.
    In another modification of the invention, known per se, holding the clamp (retainer) of the friction linings in such a U-shape that its legs are deformed in such a way that at the leading end of the brake elements, structures that form the sliding guide means 10, on one side of the brake drive. are shifted in the opposite direction to that in which they are shifted on the other side of the brake disc.
    In FIG. 1 shows a plan view from above 15 with a partial cross-section of an adjustable type disc brake with a floating bracket; in FIG. 2 - piston, which is modified in comparison with the implementation option; shown in FIG. 1; in FIG. 20 3 - section AA in FIG. 1; in FIG. 4 - guide pin on an enlarged scale: in FIG. 5 is a plan view from above with a partial section of another embodiment of a correcting type disc brake with 25 floating brackets; in FIG. 6 is a side elevational view in partial cross section of the disc brake of FIG. 5; in FIG. 7 is a plan view from above with a partial cross-section of another variant of a disc brake of a rectified type 30 with a floating bracket;
    in FIG. 8 is a side elevational view in partial section of a disc brake shown in FIG. 7; in FIG. 9 is a preferred modification of guide fingers 35 and grooves; in FIG. 9a is a partial view of figure 1 along the section along the line AB; in FIG. 10 - axial displacement of the mounting plates of the friction linings in the piston end.
    In FIG. 1 shows a brake disc 10, a support member 12 fixedly attached to a vehicle, and a floating bracket 14 in horizontal section. Two brake linings 16 and 18 can be applied on either side of the brake disc 10 and each comprise a friction liner 20 and 22 and mounting plates 24 and 26, respectively. A holding spring 28 for the mounting plates holds the lower brake pad 16 (see FIG. 1) on the floating bracket 14, while the upper brake pad 18, as seen in FIG. 1, is mounted on the piston 34 of the piston and cylinder assembly by means of a holding spring 30. The fingers 32 (Fig. 3) are parallel to the X axis of the brake disc 10 and similarly serve to attach the brake linings 16 and 18.
    The inlet channel (hole) 36 for the hydraulic fluid leads into the chamber 38 of the piston and cylinder assembly, so that the piston 34 can move parallel to the X axis in the direction of the brake disk 10. When the brake lining 18 is applied, which is directly pressed by the piston 34 to the brake disk 10. opposite the brake lining is also pressed against the brake disk by the reaction forces transmitted through the floating block 14. The slider 40 is rigidly connected to the piston 44. In the case of the variant (see FIG. 1), the slider 40 is combined with the piston 34 '. In FIG. 2 shows a modification of this embodiment, where the slider. 40 is welded to the piston 34 of a conventional design. Elastic sealing bellows 42 are sealed on the sliding surface between the piston 34 and the floating block 14.
    The support element 12, which is fixedly attached to the vehicle, has two support arms (protrusions) 44, 46, which extend vertically upward behind the brake disc (see FIG. 3). The grooves 48, 50, 52 are made in the support arms 44 and 46 and on each side of the brake disc 10. In FIG. 1 shows only three grooves 48. 50 and 52 in cross section, while the fourth groove, which corresponds to the shown groove 52, is closed by the floating block 14.
    The guide fingers 54. 56. 58 are mounted in the grooves 48, 50 and 52. The sections of the guide fingers 54, 56 and 58. protruding from the support arms 44 and 46 extend into grooves 60 (see FIG. 3), 62, 64. The guides the fingers 54 and 58 interacting with the indirectly activated brake lining 16 (in FIG. 1 below the brake disc 10) resemble guide rails 60 and 64 formed in the floating pad 14. The floating pad 14 in this way can. move parallel to the X axis of the brake disc 10.
    Guide pins 56 interacting with the directly actuated brake lining 18 extend into grooves 62. Here, the piston 34 can move relative to the support member 12 and its protrusions 44 and 46 parallel to the X axis when hydraulic pressure is generated in the chamber 38. The elastic covers 66.68 and 70 cover the sliding guides consisting of the guide fingers 54, 56, 58 and the grooves 60, 62, 64. so that the sliding guides cannot become dirty and water is prevented from entering.
    Arrow P shows the direction of rotation of the brake disc 10 while driving forward. The guide fingers 58 are larger at the leading front end of the brake than the guide fingers 54, 56 at the driven rear end of the brake. The holes 48 and 50 for the guide pin 54 and 56 at the driven end have the same diameter along their entire length. Section 78 of the guide finger (Fig. 4) can be snugly pressed in it. Section 80 of the increased diameter of the guide fingers stops at the support of the shoulder 44 and serves as a slot for covers 66 and 68. Another section 82 of the guide fingers at the driven end of the brake has an increased diameter compared to section 80 and clamps the socket covers. On the other side, a larger diameter portion 82 abuts on the other side of the grooves 60 and 62 into the floating block 14 and the slider 40, respectively, as can be seen in FIG. 3. Section 84 of the guide fingers at the driven end of the brake extends into the grooves 60 and 62, respectively.
    The protective sheets 72, 74 and 76 (a protective sheet interacting with a guide finger not shown, not shown) protect the covers from excessive heat when the brake becomes hot. The protective sheets do not cover the covers completely around, so that the space between the sheet and the cover does not become clogged with dirt.
    At the leading end of the brake (see arrow P in Fig. 3), the grooves 52 and the grooves formed in the support arm 46 are larger than the grooves 48 and 50, which are coaxially directed with the grooves 52 along axes parallel to the plane of the brake disc (Fig. 1). The increased diameter at the leading end makes it possible to have a mechanical assembly of the guides’ fingers at the driven end (the relationship can also be inverted).
    The guide pins 54, 56, 58 and not shown to be symmetrical in the rotational position and can be produced with low production costs by cold pressing. The guide fingers 58, and not shown, located at the leading end of the brake are similar to the guide fingers at the driven end shown in FIG. 4. but they are threaded and formed with a hexagonal recess at their ends, remote from the center of the brake. Guide fingers located at the leading end of the brake transmit the frictional force generated on the brake disc 10. through the thread to the support arm 46 when the vehicle is moving in the rear direction.
    The rotation of the guide fingers 58 and not shown, located on the leading end of the brake (reference in figures 1 and 3) makes it possible to have their exact positional position relative to the support arm 46. Due to this, the gap between the floating block 14 and the support element 12, which is fixedly attached to the car, It can also be precisely adjusted. The thread that is formed on said guide fingers is non-reversible. In a simplified embodiment, the adjustable guide fingers at the driving end can be replaced with the same guide fingers that are used at the driven end.
    As shown in FIG. 3, the floating block 14 is formed with protrusions 86 opposite the guide fingers, grooves 60. 62 64 and not shown are formed in these protrusions, and covers 66. 68, 70. and a cover not shown are installed between these protrusions. The floating shoe 14 is adapted to pivotally rotate around the longitudinal axes A of the guide fingers 54 and 58. The floating shoe 14 is formed with protrusions 88 on the side of the indirectly acting brake lining 16 and a mounting plate 24 of this brake lining is attached between them.
    In a manner analogous to the floating block 14, the opposing piston 34, with its slider 40, can pivotally rotate around its longitudinal axes respectively; corresponding interacting guide pin 56 and not shown. The exact adaptation of the friction linings 20 and 22 to the position of the brake disc 10 thus occurs according to circumstances. ,
    Adjustable floating disc brakes shown in Figures 5 to 8 have the same basic structure as the embodiment shown in Figures 1 to 4, especially with respect to the brake lining support. The same numeric positions apply to elements performing the same functions, so that reference can be made to the above description. However, the difference is presented by the details of the sliding guide means.
    According to figures 5 to 8, the supporting element 12. which is fixedly attached to the vehicle, contains two supporting arms (brackets 44. 46. extending vertically top above the brake disc 10. The left supporting arm 44 in Fig. 5 is formed with grooves 48, 50 with any , one side of the brake disc 10. At the leading end E of the brake, an opposing support arm 46 is also formed with two grooves 52 (of which only one is shown). The other not shown groove and the corresponding groove 52 in the support arm 56 are placed on the other side of the brake disc 10 and mounted note but symmetrically with notch 52 shown relative to the brake disk. In FIG. 5, both the groove 52 until the closed floating shoe 14.
    Two guide pins 54 and 56 are provided on the driven end A of the brake. The lower guide pin 54 in FIG. 5 is mounted directly on the floating block 14. The upper guide pin 56 (see FIG. 6) is mounted on the slider 40 of the piston 34.
    Two other guide pins 58 (of which only one is shown in FIG. 6) are mounted on the leading end E of the brake. These guide fingers are screwed into the grooves 52.
    In a vertical section (as shown in FIG. 6), the guide fingers 54. 56 provided on the driven end A of the brake are wedge-shaped with a wedge angle of 90 to 120 e *. The resulting wedge-shaped tips 96, 98, guide fingers 54, 56 come into contact (engage) with additional grooves 60, 62. which are formed in the intermediate parts 90, 92).
    At the leading end of the brake E, the guide fingers 58 have cylindrical tips 97 (of which only one is shown in FIG. 6) for contacting additional grooves formed in the intermediate parts 94) of which in FIG. 6 is shown only one) mounted on a floating block 14 at the bottom of FIG. 5 and on a slider 40 of the piston 34 at the top of FIG. 5.
    The four guide pins 54, 56.58 can thus move in the grooves 60, 62, 64 in the direction of the X axis. The wedge-shaped tips of the tips 96, 98 of the guide pins 54, 56 on the driven end A of the brake ensure that the guide means come into contact with tight installation, so it is guaranteed that the guide elements come into contact without clearance in all directions.
    The intermediate parts 90, 92, in which the U-shaped wedge-shaped grooves 60, 62 of the sliding guide means are formed on the driven end A of the brake, are attached to the shoulder 44 of the stationary support element 12 by means of fixing bolts 100, 102.
    A leaf spring 104 is provided at the leading end E of the brake (of which only one is shown, as can be seen in FIG. 6, to press the floating block 14 or piston 34 and the slider 40 against the driven end of the brake A. The leaf spring 104 rests on a step formed in guide fingers 58 and press intermediate parts 94 (of which only one is shown in FIG. 6).
    Due to the atom, the floating block 14 is pressed to the left, as can be seen in FIG. 5 and 6, using the shown leaf spring 104, while the piston 34 and its slider 40 are pressed to the left with the help of a not shown leaf spring. Sliding guides are protected from dirt and moisture by elastic covers 66, 68.70 and · another cover not shown, which corresponds to cover 70.
    The retaining clip 106 of the friction lining is U-shaped, and its two legs 108 do not coincide with the vertical axis of the brake disc 10 (FIGS. 5 and 6). As shown in the first half of FIG. 5, the leg 108 of the holding clamp 106 passes through the holes 109 in the slider 40 and the mounting plate 24 of the opposite brake lining 16 and the floating shoe 14.
    One end of the holding spring 28, located on the outside of the brake, rests on the mounting plate 24 of the brake lining 16, while the other end rests on the leg 108 of the holding clip 106. The same applies to the not shown leg 108 on the left side of the brake (not shown).
    The leg 108 of the и-shaped зажим holding clip 106 of the friction lining is bent so that when inserted into the holes in the slider 40, in the mounting plates and the floating block 14, it will induce two sliding guide means at the driving end to become twisted (rotated so as to displace the inner groove 64 of the sliding guide means at the leading end in the opposite direction, resulting in the bearing being mounted at the end with absolutely no play.
    Two guide pins 58 at the leading end E of the brake can be adjusted relative to the stationary support element 12 by means of a thread. The axial clearance of the floating pad 14, based on the axis of the guide pin 58, is adjusted approximately from 0.05 to 0.02 mm by rotation of the guide fingers 58. As explained above, the leaf springs 104 then press the wedge-shaped guide means on the driven end A of the brake each to a friend without a gap.
    A gap of about 0.02 to 0.1 mm exists in the radial direction relative to the axes of the guide fingers 58. This gap is canceled by the method. described above using the retaining clip 106 of the friction lining.
    Another embodiment of a floating-type corrective type disc brake is shown in Figures 7 and 8. It differs from the embodiment in Figures 5 and 6 only in fixing the mounting plates 24, 26 on the floating block and on the piston 34, respectively. In the case of the embodiment shown in FIG. 5 and 6, a groove is provided in the floating block 14 for receiving the corresponding mounting plate 24 during tight mounting, ’while the mounting plate 26, coordinated with the piston 34 on the opposite brake pad 18, is connected to the piston by means of a stopper 114.
    In the case of the embodiment shown in figures 7 and 8, on the other hand, each mounting plate 24, 26 has a * stopper 110 and 112, respectively, formed as a dog (latch as a result of pressing and engaging in a groove in the floating block 14 or in the piston 34 In other words, the disk brake in figures 7 and 8 corresponds to the disk brake in figures 5 and 6. and the same digital positions are used to form structural elements that perform identical functions.
    In FIG. Figure 9 shows the preferred modification of the guide pins and grooves made to prevent the floating pad from slipping out of the brake support member, especially when the corrected floating-type disc brake is being transported or stored.
    The embodiment shown in FIG. 9, among others, differs from those described above! embodiments by the fact that a separate sliding part 200 is attached using a tightly mounted pin 212 in the slider 40 (or in the floating block 14 - not shown in Fig. 9). A groove 62 is provided in the sliding part 200, which is made of hardened material. In its lower part, the groove 62 is associated with another narrower groove 63, which is axially limited (Fig. 9). With its portion 57, the guide pin 56 engages in the groove 62. This portion 57 engages in the groove 62. contains an additional small spike 59 (see also Fig. 9a), which in turn engages in an additional narrower groove 63. This spike 59 does not form a direct support between the slider (or the floating bracket 14). Instead, it serves only to prevent the guide pin 56 from ι speaking in the axial ’5 direction from the groove 62 during storage or transportation.
    The supporting element 12 (see FIG. 9) is made with a groove 13 in which the guide pin 56 is recessed. When the brake is assembled, 10 the hexagonal portion of the guide pin 56 completely fits into this groove 13. As shown in FIG. 9. The protective sheet 74 has a bulge engaging with a groove 13 in the support member 12, and an opening. fifteen
    If μ represents the coefficient of friction of the lining, represents the coefficient of friction between the lubricated and sealed support (between the guide pin and the groove) and μ represents the coefficient of friction of the piston 34 in the chamber 38, then the following may apply;
    U = R -μ (1)
    R = FU μ ο 0 (2)
    If equation (1) is represented in equation (2). then the result will be the following:
    + Μ · μ ο
    If equation (3) is substituted into equation (1). the result will be the support of the mounting plates in accordance with the invention on only one floating bracket or on one piston of the assembly by the pistons of the cylinder, as well as a description of the formation of the other four guides Slides 56, 62 between the piston 34 or the slider 40, rigidly connected to the piston, and the supporting element 12 has the advantage is that the arms h hg of the lever, as shown in FIG. 10, between the friction surfaces of the friction linings 20, 22 and the respective supports on the guide pins 54, 56 (the same applies to other supports * on the opposite side) are independent of the present state of wear of the friction linings 20.22. The arms h and g of the lever remain constant throughout the wear of the friction linings. For this reason, it can be formed as called piston displacement. This means that the axis of the piston 34 can be offset relative to the brake soybean X. This offset is placed as ΔΧ in FIG. 10.
    The peripheral frictional force U arises as a result of U = RX / z · F and is taken as the piston pressure. The reaction force R corresponding to the tail pressure G is marked in FIG. 10 and acts on the center of the friction lining, so that the wear will be symmetrical. A denotes the supporting force on the inner side of the supporting element, B is the supporting force on the outer side of the supporting element, C is the supporting force acting on the piston 34. The external peripheral force associated with the friction of the brake generates a torque on the casing (case having a radius g of the lever and stopping on the piston 34. Force C can be determined as follows:
    more:
    _ t 'μ η 1 + μ
    If tilting / tipping is prevented, all the torques with respect to the fulcrum A must be balanced, i.e. the sum of all the torques must be zero, in other words:
    ΣΜα =
    3540
    F μ. g · K__F μ, # g / l · 1 = _ + μ · μ ο f 1 + μ μ 0 f (F not applicable)
    Σ ΜΛ - Χ + Ι +, + ' μ · μ ° [and hl - ^ (/ z · Κ + μμι · 1)] = 0
    ΔΧ = Ι + τ — ϊ -! --- 1 + μ 'μο [and h -1 - (μ · К + / Ζ // 1 1)]
    Δ χ = I — — l --- 1 + μ μ ο [h--d- · ^ (K - + - / L Ί)]
    The mounting plate 26 of the friction lining at the piston end is subjected to pressure. The support in the peripheral direction of the mounting plate 16 is distributed in such a way that the mounting plate 26 is guided to the supporting element 12 by means of guide means. This means that no other guiding means is provided between the piston 34 or the structural member 40 rigidly connected to the piston and the support member 12, but is instead provided directly between the mounting plate 26 and the support member 12.
    权利要求:
    Claims (16)
    [1]
    Claim
    1. A disc brake of an adjustable type with a floating bracket for cars, comprising a floating bracket installed by means of sliding guides with the possibility of displacement relative to a bearing element made with elements for fixedly fastening it to the car, two brake linings mounted on both sides of the brake disc with the possibility of applying pressure on it and having on its surfaces remote from the disk, mounting plates with friction linings fixed to them, hydraulic cylinder p assembled with a piston and a structural element rigidly connected with it, located in a floating bracket for directly applying pressure to one of the two brake linings and applying pressure to the other of them using a floating bracket, characterized in that, in order to increase the service life, one of the mounting plates of the friction linings is mounted with support in a tangential direction directly on the floating bracket, and the other is directly on the piston of the hydraulic cylinder assembly, while the brake is equipped with additional pressure slip-governing established between the carrier member and the piston or the said 'construction element.
    [2]
    2. Brake pop. 1. different from me. that the sliding guides between the bearing element and the floating bracket have two protrusions made on either of these two elements, and two recesses on the other, made with the possibility of moving the protrusions perpendicular to the plane of the brake disc, and the additional sliding guides are rigidly connected to the piston and the bearing element, have two protrusions made on one of these two elements. and two recesses on the other of them, in which the protrusions are mounted with the possibility of movement perpendicular to the plane of the disk brake.
    [3]
    3. The brake according to claim 2, with the fact that each of the protrusions is made in the form of guide fingers attached to the supporting element and interacting with recesses in the form of grooves in the floating bracket, or piston, or a stupefied structural member firmly connected to the piston.
    [4]
    4. The brake according to claim 1, with respect to the fact that it is equipped with elastic covers,
    [5]
    5 closing slide guides.
    5. Brake pop. 1, characterized in that each of the slide rails is installed at a distance from the axis of each side of the brake disc, while
    10 sliding guides between the supporting element and the floating bracket are installed on one side of the brake disc, as well. additional sliding guides between the bearing element and the piston 15 or a structural element rigidly connected to it are placed on the other side of the brake disc.
    [6]
    6. The brake according to Claim 4. On the basis of the same. that it is equipped with protective sheets,
    20 covering elastic covers, at least on their side facing the brake linings.
    [7]
    7. The brake according to claim 6, characterized in that on the floating bracket and piston you
    25 are filled symmetrical about the axis of the slot for covers.
    [8]
    8. The brake according to Claim. 1, with the fact that each of the sliding guides at the rear end of the brake is made in
    30 in the form of a spike and groove connection, and the supporting element is made with an intermediate part rigidly connected to it, made of steel, in particular hardened.
    [9]
    9. The brake according to Claim 8, with respect to
    35 in that the connection stud is made in the form of a wedge-shaped guide finger attached to the piston or to the structural member from the side of the brake facing in the direction opposite to the direction of the nominal rotation of the brake disc, and the groove is in the form of a groove made on the supporting element or on said intermediate part.
    45
    [10]
    10. The brake according to claim 8, with the exception that the additional sliding guides between the piston or structural member rigidly connected to the last floating bracket and the supporting element 50 at the front end of the brake are made in the form of cylindrical guide fingers, which are attached to the supporting element with the possibility of interaction with corresponding grooves 55 made in the piston or in the said structural element and in a floating bracket or an intermediate part rigidly connected to the bracket.
    [11]
    11. Brake pop. 10, characterized in that it is provided with springs installed between the bearing element or the guide fingers and the floating bracket or piston from the side facing in the direction of the nominal rotation of the brake disc, to bias the floating bracket or piston in the opposite direction
    [12]
    12. The brake according to claim 2, with the proviso that at least part of the recesses in the form of grooves are made with narrower grooves located at their bases 10, bounded in the axial direction, and the guide fingers are made with protrusions interacting with narrower grooves. fifteen
    [13]
    13. The brake according to claim 2, with the fact that part of the guide fingers interacting with recesses in the form of grooves is made with barrel-shaped legs.
    [14]
    14. Brake pop. 1, characterized in that the piston is displaced tangentially in the direction of the rear end relative to the axis of the brake by a distance ΔΧ, which is determined by the following formula:
    h where I is the distance between the axis and the fulcrum of the mounting plate at the end of the piston;
    • μ - coefficient of friction between the linings and brake disc;
    '"O ~ coefficient of friction between the mounting plates and, accordingly, the piston and the floating bracket;
    / L - coefficient of friction between the piston and the hydraulic cylinder:
    h is the distance between the friction surface of the friction lining at the end of the piston and the fulcrum A at the end of the piston;
    g is the distance between the friction surface of the friction lining at the end of the floating bracket and the support of the corresponding mounting plate;
    K is the distance between the reference point at the end of the piston and the point of application of reactive force from the interaction of the friction lining at the end of the floating bracket with the brake disc, transmitted to the supporting element;
    f is the distance between the point of application of the aforementioned reactive forces and the reference point at the end of the floating bracket.
    [15]
    15. Brake pop. 1, characterized in that it is equipped with a holding clip for U-shaped friction linings, the legs of which are mounted on the brake from the side facing in the direction of the nominal rotation of the brake disc, with the possibility of shifting the grooves of the sliding guides in opposite directions.
    Priority on points:
    [16]
    01/17/86 pop.p. 1-7,
    04/30/86 pop.p, 8-15.
    36 3S
    A- /
    J7 68 36
    1ί> 38
    FIG. 10
    类似技术:
    公开号 | 公开日 | 专利标题
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    US4351420A|1982-09-28|Sliding guide for a floating caliper disc brake
    US5562187A|1996-10-08|Guide pin for a sliding caliper disc brake
    US6725980B2|2004-04-27|Apparatus and method for mounting friction elements in disc brakes
    US4560037A|1985-12-24|Spring for a disc brake
    US4306636A|1981-12-22|Floating-caliper spot-type disc brake
    EP0513310B1|2000-08-09|Pad support for disc brake assembly
    US4606439A|1986-08-19|Disc brake
    GB2033989A|1980-05-29|Floating-caliper Disc Brake
    HU188714B|1986-05-28|Disc brake for motor vehicles
    US4732242A|1988-03-22|Spot-type disc brake for vehicles
    同族专利:
    公开号 | 公开日
    IN168741B|1991-06-01|
    TR23188A|1989-05-01|
    EP0229618A2|1987-07-22|
    BR8700192A|1987-12-08|
    DE3762149D1|1990-05-10|
    CS8700213A2|1991-11-12|
    KR870007381A|1987-08-18|
    US4775033A|1988-10-04|
    PL150039B1|1990-04-30|
    JP2566231B2|1996-12-25|
    ES2014999B3|1990-08-01|
    JPS62171531A|1987-07-28|
    PL263679A1|1987-11-16|
    EP0229618A3|1988-07-20|
    CZ279699B6|1995-06-14|
    KR940001993B1|1994-03-12|
    EP0229618B1|1990-04-04|
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    RU2671424C2|2013-10-02|2018-10-31|Бендикс Спайсер Фаундейшн Брейк Ллк|Disk brake pad mounting and retention system and method|
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    RU2705864C1|2016-03-03|2019-11-12|Бендикс Спайсер Фаундейшн Брейк Ллк|Disc brake and brake pads set|GB959183A|1959-04-25|1964-05-27|Girling Ltd|Improvements relating to disc brakes|
    US3166157A|1962-04-13|1965-01-19|Bendix Corp|Spot type brake|
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    FR1459248A|1965-10-06|1966-04-29|Citroen Sa Andre|Improvements to disc brakes, in particular for motor vehicles|
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    US3768604A|1968-08-14|1973-10-30|Wagner Electric Corp|Disc brake and friction member structure|
    US3924711A|1973-09-06|1975-12-09|Daimler Benz Ag|Partial lining disk brake|
    DE2604579C3|1976-02-06|1978-11-09|Maschinenfabrik Stromag Gmbh, 4750 Unna|Automatic and stepless adjusting device for disc brakes|
    FR2406754B1|1977-10-18|1981-10-02|Citroen Sa|
    DE2750337C2|1977-11-10|1985-09-05|Alfred Teves Gmbh, 6000 Frankfurt|Partly lined disc brakes, in particular for motor vehicles|
    DE2856108C2|1978-12-23|1985-01-24|Alfred Teves Gmbh, 6000 Frankfurt|Guide for the saddle of a floating caliper disc brake|
    DE2907516A1|1979-02-26|1980-09-18|Teves Gmbh Alfred|FLOATING SADDLE PART COVER DISC BRAKE|
    DE3009002A1|1979-02-28|1981-09-24|Hermann Dr.-Ing. 7412 Eningen Klaue|Segmented full effect brake disc - has interlocking faces with connectors formed by straps outside braking area|
    DE3209389C2|1982-03-15|1990-08-23|Alfred Teves Gmbh, 6000 Frankfurt, De|
    DE8401625U1|1984-01-20|1984-08-30|Lucas Industries P.L.C., Birmingham, West Midlands|PARTIAL PAD DISC BRAKE|
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    DE102015107128A1|2015-05-07|2016-11-10|Knorr-Bremse Systeme für Nutzfahrzeuge GmbH|Disc brake of a commercial vehicle|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE8601094U|DE8601094U1|1986-01-17|1986-01-17|Floating caliper, partially lined disc brake|
    DE8611885U|DE8611885U1|1986-04-30|1986-04-30|
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