Double-piston dry type electronic mechanical braking EMB system

Abstract

The invention discloses a double-piston dry-type electronic mechanical braking EMB system, which belongs to the technical field of service braking, comprises a lower caliper frame fixed in a frame and a caliper body connected with the lower caliper frame in a sliding manner, and is characterized in that a notch for a brake disc to pass through is formed in the lower caliper frame; two friction plates arranged on the two opposite sides of the brake disc respectively are installed in the caliper body, a driving mechanism used for outputting rotating power is fixedly connected to one side of the caliper body, a transmission cavity is formed in the caliper body, and the output end of the driving mechanism extends into the transmission cavity to be fixedly connected with a driving gear. Two driven gears meshed with the driving gear are rotationally connected into the transmission cavity, the two driven gears are symmetrically arranged relative to the center of the driving gear, two piston cylinders communicating with the transmission cavity are arranged in the clamp body, and pistons are slidably connected into the piston cylinders in a limited mode; a ball screw extending into the piston cylinder is fixedly connected to the driven gear, the ball screw is sleeved with the piston in a threaded mode, and the side, away from the driving mechanism, of the piston is fixedly connected with the friction plate close to the driving mechanism.

Description

Technical Field

[0001] The invention belongs to the technical field of vehicle braking, and in particular relates to a dual-piston dry type electronic mechanical brake (EMB) system. Background Art

[0002] In the field of automobile braking technology, the electromechanical brake (EMB) uses a motor and a mechanical feed mechanism to drive the brake. The electromechanical brake has the characteristics of simple structure, sensitive response, stable load transmission, and no need to set up hydraulic pipelines, and has a high transmission efficiency. At the same time, the electromechanical brake also has a trend of miniaturization to adapt to the wheel side space of the vehicle. The existing single-piston EMB force transmission mechanism has a limited working force limit, provides a small braking torque, and the brake pad is subjected to too concentrated clamping force.

[0003] Therefore, it is necessary to propose a dual-piston dry electronic mechanical brake EMB system to solve the above problems. Summary of the invention

[0004] In view of this, the purpose of the present invention is to provide a dual-piston dry electronic mechanical brake EMB system to solve the problems in the prior art that the existing single-piston EMB force transmission mechanism has limited working force limit, provides small braking torque, and the brake pad is subjected to excessively concentrated clamping force.

[0005] In order to achieve the above object, the present invention provides the following technical solutions:

[0006] The present invention provides a dual-piston dry electronic mechanical brake EMB system, comprising: a lower caliper frame fixed in a vehicle frame and a caliper body slidably connected to the lower caliper frame, the lower caliper frame is provided with a notch for a brake disc to pass through, the caliper body is provided with two friction plates respectively arranged on opposite sides of the brake disc, one side of the caliper body is fixedly connected with a driving mechanism for outputting rotational power, a transmission cavity is provided in the caliper body, the output end of the driving mechanism extends to the transmission cavity and is fixedly connected with a driving gear, the transmission cavity is rotatably connected with two driven gears both meshing with the driving gear, the two driven gears are symmetrically arranged about the center of the driving gear, two piston cylinders respectively communicated with the transmission cavity are provided in the caliper body, a piston is limitedly slidably connected in the piston cylinder, a ball screw extending into the piston cylinder is fixedly connected to the driven gear, the piston is threadedly sleeved on the ball screw, and the piston is fixedly connected to the friction plate close to the driving mechanism at a side away from the driving mechanism.

[0007] Furthermore, the piston includes a threaded block connected to the ball screw through a ball thread, the threaded block is provided with an internal thread that cooperates with the ball screw, the threaded block is limitedly slidably connected in the piston cylinder, the threaded block is threadedly connected with a gear ring, the gear ring is fixedly connected to the friction plate near the brake disc end, a plurality of first slide grooves that are respectively connected to the key grooves are provided in the piston cylinder, a slide seat is limitedly slidably connected in the first slide groove, the slide seat is fixedly connected to the threaded block, a trapezoidal block that can slide axially along the slide seat is slidably mounted on the slide seat, a screw is rotatably connected to the bottom end of the trapezoidal block, the screw is threadedly connected to the slide seat, one end of the screw extends to the bottom end of the slide seat and is fixedly connected to a driving block, and the rotation The driving block can make the screw rotate to make the trapezoidal block move axially along the sliding seat, and a baffle that can resist the driving block is fixedly arranged in the first sliding groove, and a second sliding groove connected to the first sliding groove is arranged in the piston cylinder, and a rack that meshes with the gear ring is limitedly slidably connected in the second sliding groove, and an inclined edge that resists the trapezoidal block is arranged on the rack. Sliding the threaded block can push the sliding seat to move until the driving block resists the baffle, and continuing to slide the threaded block can make the driving block rotate to make the trapezoidal block move axially through the screw. When the friction plate returns to its position, the threaded block drives the sliding seat to return, so that the trapezoidal block slides in the direction away from the brake disc to make the rack slide, thereby making the gear ring rotate and move in the direction close to the brake disc.

[0008] Furthermore, the threaded block is provided with a plurality of keys circumferentially with the threaded block axis as the center, the piston cylinder is provided with a plurality of key slots corresponding to the keys one by one, and the threaded block is connected in the piston cylinder by limited sliding through the cooperation of the keys and the key slots.

[0009] Furthermore, a push block is fixedly connected to the key near the sliding seat, and the push block is fixedly connected to the sliding seat at an end away from the key.

[0010] Furthermore, the threaded block is provided with a threaded segment, the threaded segment is provided with an external thread, the toothed ring is threadedly connected to the threaded segment, and the diameter of the toothed ring is smaller than the diameter of the threaded block.

[0011] Furthermore, an elastic member is fixedly connected between the rack and the top wall of the second slide groove.

[0012] Furthermore, the sum of the elastic forces of the multiple elastic members is smaller than the friction force between the gear ring and the threaded segment.

[0013] Furthermore, the gear ring is rotatably connected to a rotating disk near the end of the friction plate, and the rotating disk is rotatably connected to the friction plate.

[0014] The beneficial effects of the present invention are:

[0015] 1. The present invention adds a planetary gear reduction mechanism on the basis of the single-piston EMB output to evenly distribute the torque to the two sets of ball screws, and then simultaneously pushes the two sets of pistons to transmit the clamping force to the friction plate to complete the braking. The dual-piston EMB further increases the output torque under the reduction mechanism, and further lengthens the rotation stroke to provide a faster and more delicate braking experience;

[0016] 2. The present invention uses the design of the piston to automatically compensate for wear during the next service braking, thereby ensuring that the braking clearance and the braking response are consistent.

[0017] Other advantages, objectives and features of the present invention will be described in the following description and will be apparent to those skilled in the art to some extent, or those skilled in the art may be taught from the practice of the present invention. The objectives and other advantages of the present invention may be realized and obtained through the following description. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to make the purpose, technical solution and beneficial effects of the present invention clearer, the present invention provides the following drawings for illustration:

[0019] Figure 1 It is a schematic diagram of the overall structure of an embodiment of the present invention;

[0020] Figure 2 It is a cross-sectional view of the overall structure of an embodiment of the present invention;

[0021] Figure 3 This is a schematic diagram of the matching structure of the piston cylinder and the ball screw according to an embodiment of the present invention;

[0022] Figure 4 This is a schematic diagram of the matching structure of the piston and the ball screw according to an embodiment of the present invention;

[0023] Figure 5 It is a schematic diagram of the matching structure of the rack and the trapezoidal block according to an embodiment of the present invention;

[0024] Figure 6 This is a schematic diagram of the structure in which a rack is installed in a piston cylinder according to an embodiment of the present invention;

[0025] Figure 7 It is a schematic diagram of the matching structure of the driving block and the baffle according to an embodiment of the present invention.

[0026] The markings in the accompanying drawings are as follows: lower clamp frame 1, notch 101, clamp body 2, transmission chamber 201, piston cylinder 202, drive mechanism 3, driving gear 4, driven gear 5, piston 6, threaded block 601, key 602, keyway 603, threaded segment 604, gear ring 605, first slide groove 606, slide seat 607, trapezoidal block 608, screw 609, drive block 610, baffle 611, second slide groove 612, rack 613, elastic member 614, rotating disk 615, push block 616, ball screw 7. DETAILED DESCRIPTION

[0027] like Figures 1 to 7 As shown, the present invention provides a dual-piston dry electronic mechanical brake EMB system, comprising: a lower caliper frame 1 fixed in a vehicle frame and a caliper body 2 slidably connected to the lower caliper frame 1, the lower caliper frame 1 is provided with a notch 101 for a brake disc to pass through, and the caliper body 2 is provided with two friction plates respectively arranged on opposite sides of the brake disc, with reference to an electronically controlled hydraulic integrated multi-cylinder brake caliper disclosed in application number 201810923488.3 or a shunt-type electronic mechanical brake device and a vehicle disclosed in application number 202410681141.8; in this field, the installation and matching method of the lower caliper frame 1 and the caliper body 2 and the method of frictionally braking the brake disc by means of the friction plate belong to conventional technical means in this field, so the brake disc and the friction plate are not shown in the figure, and the lower caliper frame 1, the brake disc, the caliper body 2 and the like are not described in detail. and the connection relationship between the friction plate; the innovation of the present invention lies in that a driving mechanism 3 for outputting rotational power is fixedly connected to one side of the caliper body 2, and a transmission chamber 201 is provided in the caliper body 2, so the output end of the driving mechanism 1 extends to the transmission chamber 201 and is fixedly connected to a driving gear 4, and two driven gears 5 are rotatably connected in the transmission chamber 201, both of which are meshed with the driving gear 4, and the two driven gears 5 are symmetrically arranged about the center of the driving gear 4, and two piston cylinders 202 respectively connected to the transmission chamber 201 are provided in the caliper body 2, and a piston 6 is limitedly slidably connected in the piston cylinder 202, and a ball screw 7 extending into the piston cylinder 202 is fixedly connected to the driven gear 5, and the piston 6 is threadedly sleeved on the ball screw 7, and the piston 6 is fixedly connected to the friction plate close to the driving mechanism 3 away from the driving mechanism 3.

[0028] In the present embodiment, a planetary gear set (not shown in the figure) is provided in the driving mechanism 3 for deceleration. The principle of deceleration by the planetary gear set belongs to the conventional technical means in this field and will not be repeated here; and the diameter of the driven gear 5 is larger than the diameter of the driving gear 4 to further achieve deceleration; after the driving mechanism 3 outputs the rotational power to the driving gear 4, it drives the driven gear 5 to rotate, so that the two ball screws 7 rotate synchronously to drive the piston 6 to move axially along the piston cylinder 202, thereby driving the friction plate to move to clamp the brake disc for friction braking.

[0029] This solution adds a planetary gear reduction mechanism based on the single-piston EMB output to evenly distribute the torque to the two sets of ball screws 7, and then simultaneously pushes the two sets of pistons 6 to transmit the clamping force to the friction plate to complete the braking. The dual-piston EMB further increases the output torque under the reduction mechanism while further extending the rotation stroke to provide a faster and more delicate braking feel.

[0030] In one embodiment of the present invention, the piston 6 includes a threaded block 601 connected to the ball screw 7 through a ball thread, the threaded block 601 is provided with an internal thread that cooperates with the ball screw 7, the threaded block 601 is limitedly slidably connected in the piston cylinder 202, the threaded block 601 is circumferentially provided with a plurality of keys 602 centered on the axis of the threaded block 601, the piston cylinder 202 is provided with a plurality of key grooves 603 corresponding to the keys 602, the threaded block 601 is limitedly slidably connected in the piston cylinder 202 through the cooperation of the keys 602 and the key grooves 603; the threaded block 601 A threaded section 604 is provided on the upper surface, and the threaded section 604 is provided with an external thread. A toothed ring 605 is threadedly connected to the threaded section 604. The toothed ring 605 is fixedly connected to the friction plate near the brake disc end. The diameter of the toothed ring 605 is smaller than the diameter of the threaded block 601. A first slide groove 606 which is respectively connected to a plurality of key grooves 603 is provided in the piston cylinder 202. A slide seat 607 is slidably connected in the first slide groove 606. A trapezoidal block 608 which can slide axially along the slide seat 607 is slidably installed on the slide seat 607. A screw rod 609 is rotatably connected to the bottom end of the trapezoidal block 608. The screw 609 is threadedly connected to the slide 607, and one end of the screw 609 extends to the bottom of the slide 607 and is fixedly connected to a driving block 610. Rotating the driving block 610 can rotate the screw 609 to make the trapezoidal block 608 move axially along the slide 607; a baffle 611 capable of resisting the driving block 610 is fixedly arranged in the first slide groove 606, and a push block 616 is fixedly connected to the side of the key 602 close to the slide 607, and the push block 616 is fixedly connected to the slide 607 away from the key 602, and a second slide groove 612 connected to the first slide groove 606 is arranged in the piston cylinder 202 A rack 613 meshing with the gear ring 605 is slidably connected in the second slide groove 612, and the rack 613 is provided with an inclined edge that abuts against the trapezoidal block 608. Sliding the threaded block 601 can make the push block 616 push the slide 607 to move until the drive block 610 abuts against the baffle 611. Continuing to slide the threaded block 601 can make the drive block 610 rotate. When returning, the push block 616 drives the slide 607 to return, so that the trapezoidal block 608 slides in the direction away from the brake disc, which can make the rack 613 slide, thereby rotating the gear ring 605 and moving the gear ring 605 toward the brake disc.

[0031] In this solution, when the vehicle is braked, the ball screw 7 rotates to drive the threaded block 601 to move in the direction close to the brake disc, and drives the gear ring 605 to move synchronously; when the key 602 moves along the key slot 603, it drives the push block 616 and the slide seat 607 to move in the direction close to the brake disc, until the piston 6 drives the friction plate to move to perform friction braking on the brake disc. In this process, the trapezoidal block 608 moves away from the rack 613. Since the rack 613 is engaged with the gear ring 605, and the weight of the rack 613 itself is less than the friction between the gear ring 605 and the threaded segment 604, the rack 613 cannot move and cannot drive the gear ring 605 to rotate. When the friction plate abuts against the brake disc, the drive block 610 abuts against the baffle 611. When the friction plate is worn, the piston 6 will continue to move a distance consistent with the thickness of the wear, so that the drive block 610 Continue to move, due to the resistance of the baffle 611, the driving block 610 drives the screw 609 to rotate, so that the trapezoidal block 608 moves a preset distance in the direction close to the rack 613. After the braking is completed, the piston 6 drives the slide 607 to move in the direction away from the brake disc during the return process, so that the trapezoidal block 608 moves synchronously. Since the trapezoidal block 608 moves a distance in the direction close to the rack 613 when the friction plate is lost, the height of the trapezoidal block 608 when it returns is greater than the height before the friction plate is lost. Therefore, when the trapezoidal block 608 returns to its original position, the rack 613 can be moved, so that the toothed ring 605 can rotate threadably, so that the toothed ring 605 moves a preset distance in the direction close to the brake disc to make up for the thickness of the friction plate loss, so that the wear can be automatically compensated during the next driving brake, thereby ensuring that the braking clearance and braking response are consistent.

[0032] In one embodiment of the present invention, an elastic member 614 is fixedly connected between the rack 613 and the top wall of the second slide groove 612, and the elastic member 614 is a compression spring in a stretched state to ensure that the tooth shape of the rack 613 and the tooth shape of the gear ring 605 are in a state of abutment with each other, so as to improve the response accuracy of the rack 613 driving the gear ring 605 to rotate.

[0033] In one embodiment of the present invention, the sum of the elastic forces of the plurality of elastic members 614 is smaller than the friction force between the gear ring 605 and the threaded segment 604 to prevent the elastic force of the elastic members 614 from causing the gear ring 605 to rotate when the trapezoidal block 608 is disengaged from the rack 613 .

[0034] In one embodiment of the present invention, the gear ring 605 is rotatably connected to a rotating disk 615 near the friction plate end, and the rotating disk 615 is rotatably connected to the friction plate to reduce the friction force on the friction plate during the rotation of the gear ring 605.

[0035] Finally, it should be noted that the above preferred embodiments are only used to illustrate the technical solutions of the present invention rather than to limit it. Although the present invention has been described in detail through the above preferred embodiments, those skilled in the art should understand that various changes can be made in form and details without departing from the scope defined by the claims of the present invention.

Claims

1. A dual-piston dry type electromechanical brake (EMB) system, comprising: A lower caliper frame fixed in the frame and a caliper body slidably connected to the lower caliper frame are characterized in that: the lower caliper frame is provided with a notch for the brake disc to pass through, and two friction plates respectively arranged on opposite sides of the brake disc are installed in the caliper body; a driving mechanism for outputting rotational power is fixedly connected to one side of the caliper body, a transmission cavity is provided in the caliper body, and the output end of the driving mechanism extends to the transmission cavity and is fixedly connected to a driving gear, and two driven gears are rotatably connected in the transmission cavity, both of which are meshed with the driving gear, and the two driven gears are symmetrically arranged about the center of the driving gear, and two piston cylinders respectively connected to the transmission cavity are provided in the caliper body, and a piston is limitedly slidably connected in the piston cylinder, and a ball screw extending into the piston cylinder is fixedly connected to the driven gear, and the piston is threadedly sleeved on the ball screw, and the piston is fixedly connected to the friction plate close to the driving mechanism away from the driving mechanism.

2. The dual-piston dry type electromechanical brake (EMB) system according to claim 1, characterized in that: The piston comprises a threaded block connected to the ball screw through a ball thread, the threaded block is provided with an internal thread that cooperates with the ball screw, the threaded block is limitedly slidably connected to the piston cylinder, the threaded block is threadedly connected with a gear ring, the gear ring is fixedly connected to the friction plate near the brake disc end, the piston cylinder is provided with a plurality of first slide grooves that are respectively connected with key grooves, a slide seat is limitedly slidably connected in the first slide groove, the slide seat is fixedly connected to the threaded block, a trapezoidal block that can slide axially along the slide seat is slidably mounted on the slide seat, the bottom end of the trapezoidal block is rotatably connected with a screw, the screw is threadedly connected to the slide seat, one end of the screw extends to the bottom end of the slide seat and is fixedly connected to a driving block, and the rotation of the The driving block can make the screw rotate to make the trapezoidal block move axially along the sliding seat, and a baffle that can resist the driving block is fixedly arranged in the first sliding groove, and a second sliding groove connected to the first sliding groove is arranged in the piston cylinder, and a rack engaged with the gear ring is limitedly slidably connected in the second sliding groove, and an inclined edge that resists the trapezoidal block is arranged on the rack. Sliding the threaded block can push the sliding seat to move until the driving block resists the baffle, and continuing to slide the threaded block can make the driving block rotate to make the trapezoidal block move axially through the screw. When the friction plate returns to its position, the threaded block drives the sliding seat to return, so that the trapezoidal block slides in the direction away from the brake disc to make the rack slide, thereby making the gear ring rotate and move in the direction close to the brake disc.

3. The dual-piston dry type electromechanical brake (EMB) system according to claim 2, characterized in that: The thread block is provided with a plurality of keys in the circumferential direction with the thread block axis as the center, and the piston cylinder is provided with a plurality of key slots corresponding to the keys one by one. The thread block is connected in the piston cylinder in a limited sliding manner through the cooperation between the keys and the key slots.

4. The dual-piston dry type electromechanical brake (EMB) system according to claim 3, characterized in that: The key is fixedly connected with a push block on the side close to the slide seat, and the push block is fixedly connected with the slide seat at an end away from the key.

5. The dual-piston dry type electromechanical brake (EMB) system according to claim 4, characterized in that: The thread block is provided with a thread segment, the thread segment is provided with an external thread, the toothed ring is threadedly connected to the thread segment, and the diameter of the toothed ring is smaller than the diameter of the thread block.

6. The dual-piston dry type electromechanical brake (EMB) system according to claim 5, characterized in that: An elastic member is fixedly connected between the rack and the top wall of the second sliding slot.

7. The dual-piston dry type electromechanical brake (EMB) system according to claim 6, characterized in that: The sum of the elastic forces of the multiple elastic members is smaller than the friction force between the gear ring and the threaded segment.

8. The dual-piston dry type electromechanical brake (EMB) system according to claim 7, characterized in that: The gear ring is rotatably connected with a rotating disk near the end of the friction plate, and the rotating disk is rotatably connected with the friction plate.

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