• 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:
    BRAKE LEVER FOR DRUM BRAKE. The present invention relates to a brake lever for a vehicle's drum brake comprising a lever section (2) for connection to a brake cylinder and a housing section (3) for attachment to an S-cam shaft with groove, which receives an adjustment device, the adjustment device comprising a first clutch (K1), the first clutch (K1) being provided by a first spring element (9) with a spring force and a second clutch (K2 ) formed as a one-way clutch with a number of teeth (Z2), the second clutch (K2) being propelled by a second spring element (19) with a spring force, wherein the teeth (Z2) of the second clutch (K2) are configured in such a way that the spring force applied by the second spring element (19) can move the second clutch (K2) in its fully closed position against the torques that are induced in it by friction, since the first clutch (K1) remains in an open position.
    公开号:BR112014008929B1
    申请号:R112014008929-9
    申请日:2012-10-09
    公开日:2021-03-16
    发明作者:Joakim Gripemark
    申请人:Haldex Brake Products Ab；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a brake lever for a vehicle drum brake comprising a lever portion for connection to a brake cylinder and a housing portion for attachment to a grooved S-cam shaft, and a corresponding drum brake.
    [0002] In the prior art, for example, of EP 1 064 472 B1 and EP 0 598 290 B1 of the applicant, brake levers and slack adjusters, respectively, are known to have proven to be applicable in practical service. Such brake levers comprise a lever section for connection to a brake cylinder and a housing section for attachment to an S-cam shaft with a groove that controls the two brake linings on the drum. An adjustment device is received by the brake lever housing section, which comprises a first clutch, the first clutch being provided by a first spring element with a spring force, and a second clutch, the second clutch being provided by a second spring element with a spring force as well.
    [0003] Generally speaking, the second clutch is configured as a one-way clutch and comprises a gear tooth that forms with a defined number of teeth.
    [0004] Although the accuracy of adjustment of the automatic slack adjusters according to the prior art could have been further improved in that the steps of adjusting the one-way clutch in the adjusting device have been made smaller, see, for example, WO 2011 / 016047 A1, or where even a one-way clutch with no intermediate steps has been employed, so much higher demands on safety and reliability of such systems have been met, however, there is still a need for further increase in accuracy and capacity repetition of the adjustment movements, in particular with regard to future requirements in electronic brake monitoring systems.
    [0005] In this regard, it will be peculiarly better distinguished between normal operation and malfunction of the entire brake system, and the monitoring and warning function of such brake control mechanisms will be further increased.
    [0006] One-way clutches, which perform very small steps or even work continuously, as described, for example, in WO 2011/016047 A1, clearly show disadvantages with respect to their resistance, that is, also with respect to the magnitude of the possible force transmission. In addition, its wear resistance as well as its resistance to impurities in lubricating grease is clearly reduced. Such disadvantages will be avoided.
    [0007] On the basis that it is an objective of the present invention to provide a brake lever with an integrated adjustment device for drum brakes, for which the adjustment device offers higher adjustment accuracy, in particular in terms of consistent repetition of very small adjustment steps for the clutches used by the adjustment device.
    [0008] Such an objective is solved by a brake lever according to claim 1.
    [0009] According to the invention, a brake lever for a vehicle drum brake comprises a lever section for connection to a brake cylinder and a housing section for attachment to a grooved S-cam shaft, which receives an adjustment device, the adjustment device comprising a first clutch, the first clutch being provided by a first spring element with a spring force, and a second clutch formed with a one-way clutch with several teeth, the second clutch being propelled by a second spring element with a spring force, in which the teeth of the second clutch are configured in such a way that the spring force applied by the second spring element can displace the second clutch in its fully closed position against the torques which are still induced by friction, as long as the first clutch remains in an open position.
    [0010] According to a preferred embodiment of the brake lever according to the invention, the teeth of the second clutch comprise such an angle of inclination that the second clutch can be activated in its fully closed position by means of the spring force acting on the same, in which the configuration of the teeth in the second clutch and the configuration of the second spring element are correspondingly tuned to each other.
    [0011] Because of this, it is ensured that the smallest possible adjustment steps are carried out by the circumferential arrangement, and the division of the teeth, that is, by means of their angular displacement, in the first clutch and not, as so far in the state of the art, in the second clutch that is formed as a one-way clutch.
    [0012] The adjustment device that is integrated in the housing section comprises a helical wheel for connection to the S-cam shaft with groove and an endless screw in engagement with the helical wheel, in whose endless screw a clutch wheel it is pivotally sustained, which is engaged with the endless screw through the first clutch under the influence of a spring force, in which a control arrangement is provided that applies a control movement on the clutch wheel subject to the angular position of the lever brake from a fixed, defined reference point. In this way, the control arrangement comprises the second clutch.
    [0013] The invention is aimed at both brake adjusters who cannot adjust themselves in relation to the position of the reference point, as well as automatic brake adjusters, which adjust for this automatically. For the latter, the control arrangement comprises a control disc, which is coaxially pivotally arranged in relation to the helical worm wheel and connected to a control ring having a control arm to establish the reference point for being fixed to a fixed part of the vehicle chassis, a pinion in engagement with the toothed periphery of the control disc and an adjustment screw, which is coaxial with the pinion and is in toothed engagement with the clutch wheel, in which the geometric axis of the screw endless is perpendicular to the geometric axis of the pinion and the adjustment screw.
    [0014] A driver, which is preferably cylindrical in shape, is arranged axially, but not pivotally in relation to the pinion and coaxially with it and cooperates with the adjusting screw. The one-way clutch is preferably arranged between the driver and a tooth washer, which is connected to the adjusting screw.
    [0015] The pinion, the driver and the adjusting screw are rotatably arranged on a common axis. The pinion can be formed as a hollow shaft to receive the driver, in which additionally a compression spring is arranged between the pinion and the driver.
    [0016] An adjustment device with a corresponding control arrangement, for example, is known from EP 1 064 472 B1 of the applicant, which is explicitly mentioned with the present.
    [0017] The operation of the brake lever adjustment device according to the invention will be explained in more detail below.
    [0018] The clutch wheel, which is pivotally mounted on the endless screw, forms the first clutch with it by means of surfaces comprising teeth. Since the surfaces with the teeth are usually tapered, the first clutch is also referred to as a tapered clutch. The endless screw, and thus for engagement with the conical clutch, is adjusted under pre-tension by means of a correspondingly sized compression spring.
    [0019] According to the invention the one-way clutch is designed and configured to always be self-closing, independent of all combinations of friction pairs in the adjustment device and manufacturing tolerances of its unique components. In other words, the spring acting on the one-way clutch is at least dimensioned in such a way that frictional resistances, manufacturing tolerances, etc., have no influence and are not able to prevent the second clutch from self-closing.
    [0020] Due to the fact that the one-way clutch always closes for each condition as long as the taper clutch is in an open position, it is permitted according to the invention that the taper clutch provides a canvas clearance adjustment on the inserts of brake. During brake release, it closes due to an altered tooth claw that subsequently rotates the adjusting screw, when the brake release will end.
    [0021] The adjustment resulting from the rotating adjustment screw occurs as long as the canvas clearance in the brake pads is excessive with a certain amount. This amount in turn is related to the angular division between the teeth or in other words related to the number of teeth in the taper clutch.
    [0022] In this way, the precision of adjustment in theory can be additionally increased by those skilled in the art in which the number of teeth in the taper clutch will be additionally increased. This, however, is only possible to a limited extent and generally not recommended, respectively, since an increase in the number of teeth in relation to the perimeter would result in smaller teeth which, however, may be less resistant to wear and grease impurities. lubricant.
    [0023] However, since it is ensured according to the invention that the one-way clutch always closes before the tapered clutch closes during the return stroke, the influence on the smallest possible adjustment step resulting from the angular division between the teeth in the one-way clutch and its number, respectively, can be decoupled with the result that the number of teeth in the one-way clutch can be further reduced and the size of its teeth increased, respectively, while the number of teeth of the conical clutch remains. This measurement is associated with increased device adjustment accuracy.
    [0024] With regard to the one-way clutch this means that larger teeth can be used which, together with cost reduction, are easier to manufacture on the one hand, and which comprise improved tooth strength and higher wear resistance on the other hand.
    [0025] The adjustment made by the taper clutch occurs at that point, when the taper clutch rotated from its original upper teeth engagement to lower teeth, in which the upper teeth are in engagement with the corresponding lower teeth of the respective opposing teeth, at least for one contact of upper tooth with upper tooth, in which the upper teeth of the teeth are in contact with the upper teeth of the respective opposing teeth. From that position, the conical clutch can then slide, according to the direction of rotation, for the upper teeth to grasp on adjacent lower teeth, next, in which the upper teeth are again engaged with the corresponding lower teeth of the respective pair of teeth. next, and in that way, the clutch closes.
    [0026] This top-to-top position, in which the upper teeth are in contact with the upper teeth of the respective opposing teeth, corresponds to a 360 / (2 * Z1) degree clutch wheel rotation and a screw rotation adjustment range of U * 360 / (2 *) degrees, where Z1 is the number of teeth of the tapered clutch and U is the gear ratio between the clutch wheel and the adjusting screw which is defined by U = Z3 / Z4 , where Z3 is the number of teeth on the clutch wheel and Z4 is the number of teeth or entries on the adjusting screw.
    [0027] In a preferred embodiment of the invention the one-way clutch is configured so that in its closure it can create at least the above-explained rotation of the clutch wheel without having been close to overtaking on its own teeth just before, that is, shortly before both toothed surfaces of the one-way clutch, which are relatively mobile against each other, are sliding through a circumferential tooth position. Overtaking corresponds to a rotation of the adjusting screw in relation to the pinion of 360 / Z2 degrees, whereas Z2 is the number of teeth of the one-way clutch.
    [0028] Thus, this means for a rotation of the adjustment screw that 360 / Z2 degrees = U * 360 / (2 + Z1) degrees applies, so the ratio of the number of teeth is as follows: Z2 = 2 * Z1 / U (1)
    [0029] The Z2 number of teeth of the one-way clutch should therefore be twice the number of Z1 teeth of the tapered clutch in relation to the gear ratio between the clutch wheel and the adjusting screw.
    [0030] If the one-way clutch is close to overtaking, the contact areas between the teeth become very small and the risk of tooth breakage and excessive wear increases substantially. For this reason, the number of teeth Z2 of the one-way clutch must be less than as defined in equation (1) above, which is why according to the invention the number of teeth Z2 will preferably be 75% of the same and more preferably 50% of the same. That is why it is ensured that overtaking the one-way clutch is avoided with good margins in all adjustment steps, which come from normal canvas wear.
    [0031] To ensure that the one-way clutch is self-closing, the torque produced by the spring force from the spring element acting on the one-way clutch which, according to the invention, acts on the tooth surfaces comprising a defined inclination will overcome all frictional torques acting on the adjustment screw against the desired closing speed.
    [0032] Such frictional torques, for example, can be calculated from the drive torque of the one-way clutch, from the axial frictional force between the pinion and the driver, as well as from the frictional torques entirely generated by the elements. spring in the system.
    [0033] According to the invention, it does not matter whether the one-way clutch closes during brake application after the taper clutch has opened or if the one-way clutch closes during brake release before the taper clutch closes. It is sufficient that the suggested solution according to the invention ensures that closing the one-way clutch is delayed until the brake is released so that the frictional torques that appear on the clutch wheel and to some extent the frictions that occur on the adjusting screw assist in closing the one-way clutch instead of resisting it, so the accuracy and reliability of the adjusting device are additionally increased. Such frictional contributions can be ignored in the torque analysis.
    [0034] Such analysis must be conducted for each peculiar construction of a brake lever according to the invention subject to manufacturing tolerances, the friction pairings to be expected and perhaps some experiments for the design of single components, to ensure that according to the invention the angle of inclination of the teeth of the one-way clutch is selected in such a way that you can always be moved to its fully closed position as long as the first clutch remains in an open position.
    [0035] As explained above, the parameters to be considered for such analysis, among others, include the driving torque generated by the one-way clutch, the frictional force between the pinion and the driver and the frictional forces induced by the elements of spring, which together can be calculated.
    [0036] The driving torque produced by the one-way clutch can be calculated as Md = Rt * (Fs - Fd) * tan (α - arctan (μ)) (2) Where Rt = average tooth contact radius, Fs = axial spring force acting on the one-way clutch, Fd = axial frictional force between pinion and driver, α = angle of inclination of teeth, and μ = coefficient of friction in contact of teeth.
    [0037] The frictional force between the pinion and the driver can be additionally calculated as: Fd = μ * (Md + Ma) / Rd (3) Where Ma = additional torque acting on the driver (which, for example, can be generated by a torsion spring as, for example, known from EP 0 598 290 B1 of the applicant), Rd = radius of the ridges and notches in the pinion actuator coupling, e = friction coefficient between the actuator and the pinion, so it is assumed that it is equal to the coefficient of friction in the contact of teeth.
    [0038] By combining equations (2) and (3), we obtain Md = Rt * (Fs - μ * (Md + Ma) / Rd) * tan (α - arctan (μ)) (4),
    [0039] Which is equivalent to Md = Rt * (Fs - μ * (Ma / Rd)) * tan (α - arctan (μ)) / (1 + μ * (Rt / Rd) * tan (α - arctan ( μ))) (5).
    [0040] The frictional torques that arrive from the single spring elements in the set can be calculated for each effective contact surface as Mf = Ff * μf * Rf (6) Where Ff = axial spring force acting on the effective contact, μf = coefficient of friction in the effective contact, and Rf = average radius of the effective contact.
    [0041] Starting from the calculation possibilities resulting from the equations identified above (2) to (6), these friction torques, which can neutralize the closing of the one-way clutch according to the invention, can be calculated in more detail . The drive torque Md must always be greater than the sum of all friction torques Mf. To the extent that these frictional torques will not become below a certain value for other purposes, these frictional torques Mf should, whenever possible, therefore be further reduced or even completely eliminated by appropriate measures with respect to design and dimensioning.
    [0042] Advantages and additional features of the invention become evident from the description of the modalities as shown in the attached drawings.
    [0043] Figure 1 shows partially in cross section an example of a brake lever for a drum brake according to the prior art;
    [0044] Figure 2 is a perspective view of a brake lever for a drum brake;
    [0045] Figure 3 is a perspective view of the rotating components, internal to the adjuster;
    [0046] Figure 4 is a partially cross-sectional view of a first modifier of the adjuster according to the invention;
    [0047] Figure 5 is a partially cross-sectional view of a second modality of the adjuster according to the invention; and
    [0048] Figure 6 is a partially cross-sectional view of the adjuster as shown in figure 3 according to the invention.
    [0049] Figure 1 shows a brake lever for a drum brake according to the prior art, as known, for example, from EP 1 064 472 B1 of the applicant.
    [0050] Brake lever 1 is divided into an upper lever section 2 for connection to a brake cylinder (not shown) and a lower housing section 3 for attachment to a grooved S-cam shaft (also not shown) ).
    [0051] The housing section 3 is for receiving the adjustment mechanism which includes a helical rotating wheel 4 comprising a profile with internal grooves 4 'for cooperation with a grooved S-axis. In engagement with this helical wheel 4, an endless screw 5 is provided which is pivotally arranged in the housing section 3 and perpendicular to it.
    [0052] The end of the worm screw 5 (on the left side in figure 1) extends from the housing section 3 to the outside and the worm screw 5 is provided here with a hexagonal tool claw 5 ', as well as shown in figure 2, for manual rotation of the worm screw 5. At this end, there is a threaded cover 6 in the housing section 3 around the worm screw 4.
    [0053] A clutch wheel 7 is pivotally mounted on the worm screw 5 and on one side supported against the cover 6. On the opposite side, toothed surfaces 8 with a number of teeth Z1 cooperating with each other are provided both on the clutch wheel 7 and on worm screw 5, which together form a first clutch K1. Since the opposing surfaces 8 with teeth Z1 are conically formed which, however, is not mandatory, the first clutch K1 is also referred to as a so-called tapered clutch.
    [0054] In the presentation of figure 1 the worm screw 5 is propelled to the left by means of a strong compression spring 9 so that it engages with the conical clutch K1 is allowed. The compression spring 9 is arranged between a spring washer 10 at the end of the worm screw 5 and a threaded spring cover 11 in the housing section 3.
    [0055] A control arrangement 12 to 14 is arranged in the same opening of the housing section 3 as the helical wheel 4, but is not connected to it. The control arrangement comprises a rotating control disc 12, which has a toothed periphery, as can be seen in figure 3. The control disc 12 is provided with an external control ring 13 having a control arm 14 extending from the same. A simple cover 15 is disposed between the control disc 12 and the control ring 15 and is screwed onto the housing section 3 for swiveling support of the entire control arrangement. The control arm 14 is connected to a fixed rigid part of the vehicle chassis on which the brake lever 1 is pivotally mounted. The purpose of the control arrangement is to provide a reference or control signal for brake lever 1, as will be explained below.
    [0056] As can be seen from figures 3 to 6, a pinion 16 that is pivotally mounted on an axis 17 in the housing section 3, is engaging with the toothed periphery of the control disc 12. Pinion 16 is hollow and it receives an actuator 18 inside, which is slidable, but not pivotally arranged inside the pinion 16, for example, by means of a grooved connection, so that the actuator 18 is movable in relation to the pinion 16. A compression spring 19 between pinion 16 and driver 18 adjusts driver 18 under pre-tension to the left of the view as shown in figure 6.
    [0057] An intermediate tooth washer 20 is movably arranged on the axis 17 to the left of the actuator 18. Surfaces with a number of teeth Z2, which face each other on the actuator 18 and the intermediate washer 20, together form a second clutch K2 , which is configured as a one-way clutch and which is shown in figures 3 to 6 in its hitch, that is, in its fully closed position.
    [0058] An adjusting screw 21 being engaged with the clutch wheel 7 on the worm screw 5 is arranged on the intermediate washer 20 so as to be rotatable with it as a unit, in which a blind connection with a groove between these components can be used. Alternatively, it is also possible to supply the adjusting screw 21 and the intermediate washer 20 as a single element.
    [0059] In the modality shown in figure 6 that reveals an adjustment device that uses a rotating control distance, such as this, for example, is carried out in EP 0 598 290 B1 of the applicant, to which it is explicitly referred to herein, the axis 17 is adjusted under pre-tension by means of a spring washer 22 arranged therein, in which a spring element 23 is supported between the spring washer 22 and a housing bore in the housing section 3. The spring element 23, preferably a compression screw spring, is made relatively strong to keep the entire arrangement in and around the axis 17 free from vibration and in correct alignment and position even at very large manufacturing tolerances. For this purpose, the spring washer 22 is supported against a first backrest 24 of the shaft 17. The adjusting screw 21 is in turn supported against a second backrest 25 of the shaft 17. Where the axial length of the adjusting screw 21 will be dimensioned a little shorter than the axial distance between the two abutments 24 and 25, the spring element on the left side 23 does not apply a force on the adjusting screw 21, so that only the compression spring 19 introduces a force on the adjusting screw 21 to keep the one-way clutch K2 under a corresponding propensity and pre-tension.
    [0060] This spring force that performs the pre-tensioning is less than the spring force of the spring element 23 so that in this way the restricted friction torque can be reduced, with the backrest 24 being on the left outer side can be located in a corresponding position on axis 17.
    [0061] To always ensure according to the invention that the one-way clutch K2 is self-closing, the latter comprises an inclination of the inclination angle of the teeth Z2 which is made greater as was the case in the prior art, or the force of spring for the pre-tensioning of the K2 clutch of the compression spring 19 is also made stronger as it has been in practice until now, when compared to one-way clutches having recently been employed with brake levers for drum brakes.
    [0062] This dimensioning of the declination angles of teeth Z2 and / or of the spring element 19 can result in the one-way clutch K2 generating a higher actuation torque at the beginning of the brake actuation, which is not desired since this torque Larger drive will be transmitted over the worm screw 5 through clutch wheel 7 and conical clutch K1 and could cause the worm screw 5 to be turned first in a direction that corresponds to an increase in the canvas clearance in the brake pads.
    [0063] In particular, in order to avoid this undesirable rotation it is provided according to the invention that the spring washer or washer 10 between the compression spring 19 and the auger 5 is arranged and designed in such a way that exactly such torque of defined brake friction is applied to the worm screw 5, which is able to prevent such rotation.
    [0064] As can be seen in the embodiment shown in figure 4, the washer 10 is formed in such a way that it cooperates with the end of the front side of the auger 5 through a conical surface 26. Alternatively, the washer 10 can comprise such contact surface than the contact and with it the introduction of force in the worm screw 5 is limited to a radius that almost corresponds to the diameter of the support of the worm screw 5, that is, its diameter at the left end with which the worm screw 5 is pivotally supported in a hole in the housing section 3. For this purpose, the washer 10, for example, comprises a protruding ring 27 that surrounds a circumferential nose 28 at the end of the front side of the worm screw 5.
    权利要求:
    Claims (8)
    [0001]
    1. Brake lever (1) for a vehicle's drum brake comprising a lever section (2) for connection to a brake cylinder and a housing section (3) for attachment to a grooved S-cam shaft, receiving an adjustment device, the adjustment device comprising a first clutch (K1), the first clutch (K1) being propelled by a first spring element (9) with a spring force, and a second clutch (K2) formed as a one-way clutch with a number of teeth (Z2), the second clutch (K2) being propelled by a second spring element (19) with a spring force, characterized by the fact that the teeth (Z2) of the second clutch (K2) comprises an angle of inclination and the second spring element (19) is configured to apply a spring force, the angle of inclination and spring force of which are tuned together, so that the second clutch (K2) is adapted to generate a drive torque (Md), which is always greater than and the sum of all friction torques (Mf), which are induced to the friction adjustment device for each condition, the driving torque (Md) displacing the second clutch (K2) to its fully closed position since the first clutch (K1) remains in an open position.
    [0002]
    2. Brake lever according to claim 1, characterized in that the adjustment device comprises a helical wheel (4) for connection with a grooved S-cam shaft and an endless screw (5) in engagement with the helical wheel (4), the worm screw (5) comprising a clutch wheel (7) pivotally mounted on it, which is engaged with the worm screw (5) by means of the first clutch (K1) under application of a spring force of the first spring element (9), in which a control arrangement is provided that transmits a control movement towards the clutch wheel (7) subject to the angular position of the brake lever (1) in relation to to a fixed reference point, and where the control arrangement comprises the second clutch (K2).
    [0003]
    3. Brake lever, according to claim 2, characterized by the fact that the control arrangement comprises a control disc (12) being swiveled coaxially to the helical wheel (4) and connected to a control ring (13) comprising a control arm that is connected to a fixed part of the vehicle chassis to define a reference point, a pinion (16) being engaged with the control disc (12) by means of a toothed connection, and a screw adjustment screw (21) being coaxially arranged with the pinion (16) and connected to the clutch wheel (7) by means of a toothed connection, in which the geometric axis of the endless screw (5) is directed perpendicular to the common geometric axis of the pinion (16) and adjusting screw (21).
    [0004]
    Brake lever according to any one of claims 1 to 3, characterized by the fact that the first clutch (K1) comprises a number of teeth (Z1) on tapered surfaces (8) as well as the worm (5) as the clutch wheel (7).
    [0005]
    5. Brake lever according to claim 4, characterized in that the number of teeth (Z2) of the second clutch (K2) is less than 2 x Z1 / U, preferably less than 1.5 x Z1 / U and in particular less than 1.0 x Z1 / U, where U is the gear ratio between the clutch wheel (7) and the adjusting screw (21).
    [0006]
    6. Brake lever according to any one of claims 1 to 5, characterized by the fact that the first spring element (9) applies the spring force through a washer (10) over the end of the auger ( 5), in which the washer (10) is configured in such a way that the force contact is restricted to a tapered surface (26) and / or to a radius that almost corresponds to a worm support diameter (5) .
    [0007]
    Brake lever according to any one of claims 1 to 6, characterized by the fact that the spring force acting on the adjusting screw (21) is only provided by the spring force acting on the second clutch ( K2).
    [0008]
    8. Drum brake for a vehicle, in particular for a heavy ground vehicle, characterized by the fact that it comprises a brake lever (1) for the grooved S-cam shaft as defined in any one of claims 1 to 7.
    类似技术:
    公开号 | 公开日 | 专利标题
    BR112014008929B1|2021-03-16|brake lever for drum brake
    EP3120038B1|2019-09-11|Disc brake and brake actuation mechanism for a disc brake
    KR100310095B1|2001-12-28|Valve timing control device of engine
    TWI558608B|2016-11-21|Actuator device for a bicycle gearshift and nut for such a device
    EP3071861B1|2018-01-10|Sensor device and disc brake comprising a sensor device
    JP5541630B2|2014-07-09|Electric swing plug door operator with auxiliary door lock mechanism
    CN100516583C|2009-07-22|Disc brake with automatic adjustment
    ES2656121T3|2018-02-23|Actuator with irreversible screw-nut system, drum brake and braking device equipped in this way
    BR112014012984B1|2021-04-20|accumulator spring brake cylinder with emergency release device
    EP2669458B1|2020-03-04|Actuated flap assembly
    WO2013044892A1|2013-04-04|Readjustment device for a disk brake
    KR20100124249A|2010-11-26|Automotive applications of automatic adjustment arm
    CZ295559B6|2005-08-17|Brake lever
    ES2673554T3|2018-06-22|Brake application device for a disc brake activated by rotating lever
    BR112015021285B1|2021-09-08|VARIABLE VALVE TRAIN TO DRIVE A VALVE OF AN INTERNAL COMBUSTION ENGINE, USE OF VALVE TRAIN AND INTERNAL COMBUSTION ENGINE
    EP3073155B1|2017-06-14|A device for inhibiting selection of one or more operative positions of a selector of an automatically operated gearbox, for example a parking position
    US8490508B2|2013-07-23|Folding-top drive
    TWI729124B|2021-06-01|Actuator device for a bicycle gearshift and respective bicycle gearshift
    JP6765716B2|2020-10-07|Hinge assembly
    DE102005058042A1|2006-07-13|Motorized braking device for a vehicle
    BR102020008272A2|2021-11-09|ELECTRO-HYDRAULIC DISC BRAKE
    ES2892294T3|2022-02-03|Lid fitting for pivoting fixing of a lid to a furniture body
    DE102009036222B4|2013-02-21|Inner shoe brake with thermally controlled adjusting device for the brake shoe clearance
    KR20210047809A|2021-04-30|Electromechanical parking lock actuator
    CN110388157A|2019-10-29|The valve control device of two sides for door closer
    同族专利:
    公开号 | 公开日
    US20140216865A1|2014-08-07|
    CN103782055A|2014-05-07|
    EP2766629A1|2014-08-20|
    US9360070B2|2016-06-07|
    BR112014008929A2|2017-04-25|
    WO2013053718A1|2013-04-18|
    EP2766629B1|2017-04-05|
    TR201209278U|2012-10-22|
    CN103782055B|2016-09-28|
    DE202011106746U1|2011-12-05|
    CN203023360U|2013-06-26|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    SE420014B|1979-12-13|1981-09-07|Sab Automotive Ab|BRAKE HEAT FOR A TRUMBROMS|
    SE470526B|1992-11-18|1994-07-04|Haldex Ab|Brake lever for an S-cam brake on a road vehicle|
    SE512102C2|1998-03-27|2000-01-24|Haldex Brake Prod Ab|Control arrangement for a brake lever|
    RU2398986C2|2005-11-14|2010-09-10|Общество С Дополнительной Ответственностью "Дискомс"|Automotive brake regulator|
    TR200805758A2|2008-08-05|2009-04-21|Aydinsan Fi̇ren Circirlari Ve Otomoti̇v Yedek Parçalari İmalati Pazarlama Ve Satişi Sanayi̇ Ve Ti̇caret Li̇mi̇ted Şi̇rketi̇|FUNCTIONAL FULL AUTOMATIC BRAKE SPEED ADJUSTMENT|
    US8672101B2|2008-11-18|2014-03-18|Bendix Spicer Foundation Brake Llc|Automatic slack adjuster with clutch release cam|
    CN101526116B|2009-03-24|2012-03-07|隆中控股集团有限公司|Automatic adjusting arm of automobile|
    EP2480798B1|2009-08-03|2020-09-23|Madras Engineering Industries Private Limited|An automatic brake adjuster for adjusting the slack between the brake lining and brake drum of a vehicular braking system|
    TR200907444A2|2009-10-01|2010-03-22|Büyük Eker Bi̇jon Sanayi̇ Ve Ti̇caret Anoni̇m Şi̇rketi̇|Drive angle adjustment device|
    DE202011106746U1|2011-10-14|2011-12-05|Haldex Brake Products Ab|Brake lever for a drum brake|DE202011106746U1|2011-10-14|2011-12-05|Haldex Brake Products Ab|Brake lever for a drum brake|
    CN104698023B|2015-02-25|2017-05-03|中国科学技术大学|Remote tuning device for electron paramagnetic resonance probe|
    EP3093518B2|2015-05-11|2022-01-12|ZF CV Systems Europe BV|Readjustment unit for an automatic rod positioner|
    USD770343S1|2015-06-16|2016-11-01|Haldex Brake Products Ab|Brake adjuster|
    USD770346S1|2015-06-16|2016-11-01|Haldex Brake Products Ab|Brake adjuster|
    USD770344S1|2015-06-16|2016-11-01|Haldex Brake Products Ab|Brake adjuster|
    USD770345S1|2015-06-16|2016-11-01|Haldex Brake Products Ab|Brake adjuster|
    DE102015010348A1|2015-08-06|2017-02-09|Man Truck & Bus Ag|Device for fastening a wear sensor to a brake lever of a vehicle brake|
    CN106838071A|2016-03-16|2017-06-13|倪世荣|Helical teeth worm and gear self-adjustable arm for adjusting automobile brake clearance automatically|
    CN109563896A|2017-05-31|2019-04-02|马德拉斯工程工业私人有限公司|Automatic slack adjuster|
    USD860890S1|2017-06-10|2019-09-24|Wabco India Limited|Slack adjuster|
    USD860891S1|2017-06-10|2019-09-24|Wabco India Limited|Slack adjuster|
    US10378604B2|2017-12-07|2019-08-13|Bendix Spicer Foundation Brake Llc|Slack adjuster for a drum brake of a vehicle air braking system|
    US10704630B2|2018-05-14|2020-07-07|Bendix Spicer Foundation Brake Llc|Automatic slack adjuster with adjusting clutch in control train|
    CN109058325B|2018-10-25|2019-12-20|项炳海|Quick brake mechanism for automobile|
    CN109281967B|2018-11-26|2020-01-07|王军|Automatic brake clearance adjusting device of brake and drum brake|
    DE102019005094B3|2019-07-23|2020-09-03|Haldex Brake Products Ab|Adjustment unit for a brake and manufacturing process therefor|
    CN111765190B|2020-06-08|2022-02-18|中国航发北京航科发动机控制系统科技有限公司|Pretightening force adjusting and setting device|
    法律状态:
    2018-12-11| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|
    2020-06-16| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|
    2021-01-05| B09A| Decision: intention to grant|
    2021-03-16| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 09/10/2012, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    DE202011106746.0|2011-10-14|
    DE202011106746U|DE202011106746U1|2011-10-14|2011-10-14|Brake lever for a drum brake|
    PCT/EP2012/069980|WO2013053718A1|2011-10-14|2012-10-09|Brake lever for drum brake|
    [返回顶部]