Brake and electromechanical brake device

Abstract

The application provides a brake and an electromechanical brake device. The brake comprises a caliper body, a screw assembly, a driving motor and a brake block. The caliper body has an axially protruding stepped end portion. The screw assembly comprises a screw shaft and a screw nut. A first part of the screw shaft and the screw nut is connected to the driving motor through the stepped end portion, and a second part of the screw shaft and the screw nut is matched with the brake block. The brake further comprises a force sensor, which comprises a ring-shaped main body, an outer peripheral wall located at the outer periphery of the main body, and a sensitive part arranged in the main body and connected to the outer peripheral wall. The main body is arranged between the stepped end portion and the first part, and the outer peripheral wall is axially pressed between the stepped end portion and the first part. At least one fastener is arranged in the main body and axially extends into a through hole of the caliper body. The outer periphery of the fastener is provided with a plurality of blocking pieces which are axially distributed and matched with the through hole. The application can realize stable installation of the force sensor in a limited space, and ensure accurate detection of the force value signal.

Description

Technical Field

[0001] This application relates to the field of braking technology, and more specifically, to brakes and electromechanical braking devices. Background Technology

[0002] In brake systems, force sensors are required to monitor force values ​​in real time to meet the precise control requirements of braking force. However, due to the compact internal space and limited installation structure of brake calipers, force sensors often lack reliable and stable mounting methods. Under actual working conditions, an unstablely mounted force sensor is highly susceptible to impacts and repeated collisions from adjacent components (such as lead screw shafts, caliper housings, etc.), causing the force sensor to shift or move. This not only introduces additional signal noise and reduces the accuracy of force value detection, but also increases the risk of force sensor failure due to mechanical wear.

[0003] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0004] This application provides a brake and an electromechanical braking device that enables the stable installation of a force sensor within a limited space and ensures the measurement accuracy of the force sensor.

[0005] According to one aspect of this application, a brake is provided, comprising a clamp body, a lead screw assembly assembled in the clamp body, a drive motor, and a brake block; the clamp body has a stepped end protruding axially toward the lead screw assembly, the lead screw assembly including a lead screw shaft and a lead screw nut, a first component of the lead screw shaft and the lead screw nut passing through the stepped end and connected to the drive motor, and a second component cooperating with the brake block, the stepped end supporting the first component via a first bearing; the brake further comprises: a force sensor including an annular body portion, an outer peripheral wall located on the outer periphery of the body portion, and a sensitive component disposed in the body portion and connected to the outer peripheral wall, wherein the body portion is disposed between the stepped end and the first component, and the outer peripheral wall is axially pressed against the space between the stepped end and the first component; and at least one fastener disposed in the body portion and extending axially into a through hole in the clamp body, wherein the outer periphery of the fastener is provided with a plurality of axially distributed baffles that cooperate with the through hole.

[0006] The outer peripheral wall of the force sensor serves as the primary load-bearing interface, axially pressing against the stepped end of the clamp body and the first component (rotating component) of the lead screw assembly. This ensures that the braking reaction force is accurately transmitted axially through the outer peripheral wall to the sensitive component of the force sensor, guaranteeing the accuracy of force sensing. Furthermore, through the insertion and engagement of fasteners and through holes, the main body of the force sensor is reliably constrained axially within the clamp body, preventing it from shifting or rotating under braking vibration or impact loads. This ensures the stable pressing state of the outer peripheral wall, thereby guaranteeing that the force signal output by the sensitive component accurately and continuously reflects the braking state. Unlike rigid fixing methods, the elastic deformation of the baffle provides a small preload for fixing, preventing excessive assembly stress from being transmitted to the sensitive component of the force sensor and improving the detection accuracy of the force sensor.

[0007] In some embodiments, the plurality of baffles includes at least one first baffle and at least one second baffle that extend obliquely toward and away from the main body, respectively, and one of the first baffles and one of the second baffles abut against two opposite end faces of the through hole in the axial direction.

[0008] During braking, the fastener uses the bidirectional constraint of the first and second baffles to continuously apply a small bidirectional preload in the axial direction. This prevents the detection accuracy of the sensitive components from being affected by excessive preload, and effectively suppresses the movement and displacement of the force sensor caused by mechanical vibration, impact loads, etc., ensuring that the force sensor is always in a stable and correct sensing position, and guaranteeing the accuracy and reliability of the force signal.

[0009] In some embodiments, both the first baffle and the second baffle are annular and have an outer diameter larger than the inner diameter of the through hole, wherein: the first baffle is located at the distal end of the fastener and extends obliquely from the outer periphery of the fastener toward the body portion, and the first baffle is used to abut axially against the end face of the through hole away from the force sensor; the second baffle is located at the proximal end of the fastener and extends obliquely from the outer periphery of the fastener away from the body portion, and the second baffle is used to abut axially against the end face of the through hole near the force sensor.

[0010] When the fastener is inserted into the through hole, the first annular baffle evenly abuts against the far end face of the through hole, and the second annular baffle evenly abuts against the near end face of the through hole. Through continuous annular contact, the fastener is effectively prevented from radially deflecting or tilting in the through hole, ensuring that the force sensor can maintain strict axial alignment when subjected to asymmetric lateral forces.

[0011] In some embodiments, the outer diameter of the second baffle is larger than the outer diameter of the first baffle, the number of the second baffle is one, and the number of the first baffle is multiple.

[0012] The second baffle is located at the proximal end and does not need to pass through the through hole during assembly. Its larger outer diameter provides a larger bearing area, allowing it to firmly abut against the end face of the through hole and preventing it from sinking into the through hole. The first baffle is located at the distal end and needs to pass through the through hole. Its smaller outer diameter ensures that the compression of the first baffle by the inner wall of the through hole is moderate, facilitating installation and allowing the first baffle to rebound smoothly to abut against the end face of the through hole.

[0013] In some embodiments, both the first baffle and the second baffle are elastic baffles.

[0014] The elastic baffle can undergo recoverable bending or compression deformation when subjected to external force, and can return to its initial shape or close to its initial shape after the external force is removed, thereby achieving low assembly stress, self-locking and vibration compensation functions.

[0015] In some embodiments, the first baffle and the second baffle are tilted at an angle of 30° to 60° relative to the radial direction.

[0016] By limiting the tilt angle to the range of 30° to 60°, both ease of installation and a stable axial bidirectional self-locking mechanism can be formed after the baffle springs back.

[0017] In some embodiments, at least one end face of the through hole is provided with a recessed fitting structure, which is used to abut against the inclined surface of the corresponding baffle to form axial and radial limiting of the corresponding baffle.

[0018] The concave mating structure provides a mating surface with a geometrically compatible shape for the inclined surface of the baffle, resisting vibration and impact loads during the operation of the brake, effectively suppressing the shaking of the fastener, and thus ensuring that the pressure state between the outer peripheral wall of the force sensor and the stepped end of the clamp body and the first component remains constant, the force transmission path is accurate, and the force value sensed by the sensitive component can truly reflect the actual braking force.

[0019] In some embodiments, the first component includes two shaft portions with different radial dimensions, wherein: the first shaft portion passes through the end of the step and connects to the drive motor, the second shaft portion cooperates with the second component, and the end of the step extends axially between the first shaft portion and the second shaft portion; the main body portion is sleeved on the first shaft portion and located between the connecting end face between the first shaft portion and the second shaft portion and the axial end face of the end of the step portion facing the connecting end face, and the outer peripheral wall is pressed against the connecting end face and the axial end face; the main body portion is axially recessed relative to the outer peripheral wall, and the sensitive component is used to sense the axial force on the outer peripheral wall.

[0020] The first component utilizes two shafts with different radial dimensions to form an axial force-bearing surface (i.e., a connecting end face). The force sensor is installed between the connecting end face of the first component and the axial end face of the clamp body. The transmission path of the braking reaction force is short and the rigidity is high, which helps to achieve accurate detection.

[0021] In some embodiments, the first component is a lead screw shaft, and the second component is a lead screw nut. In the lead screw assembly, the lead screw shaft is connected to a drive motor and rotates; the lead screw nut is threaded to the lead screw shaft and translates axially. The force sensor is axially pressed between the connecting end face of the lead screw shaft and the axial end face of the clamp body.

[0022] In some embodiments, the first component is a lead screw nut, and the second component is a lead screw shaft. In the lead screw assembly, the lead screw nut is connected to the drive motor and rotates; the lead screw shaft is threadedly engaged with the lead screw nut and translates axially. The force sensor is axially pressed between the connecting end face of the lead screw nut and the axial end face of the clamp body.

[0023] In some embodiments, the outer peripheral wall is pressed against the connecting end face via a second bearing; wherein, there may or may not be an axial clearance between the outer peripheral wall and the second bearing.

[0024] The second bearing allows the rotational freedom of the first component relative to the force sensor to be unrestricted, while simultaneously transferring the axial load of the first component to the outer peripheral wall through rolling contact. This avoids the frictional torque and wear that may occur from direct contact between the first component and the force sensor, thereby minimizing the impact on the sensor's detection accuracy.

[0025] In some embodiments, the outer peripheral wall is pre-pressed axially between the step end face and the connection end face, so that the force sensor is subjected to a certain initial pre-pressure in the non-braking state, which can eliminate assembly gaps and enable the force sensor to immediately and accurately sense the force signal when the braking reaction force is applied.

[0026] In some embodiments, the main body is spaced on the first shaft, and the two are not in direct contact in the radial direction. This avoids frictional torque and frictional heat between the first shaft and the force sensor when the first shaft rotates at high speed, prevents the force sensor from losing its force measurement accuracy due to thermal drift and wear, and ensures the transmission efficiency of the lead screw assembly.

[0027] In some embodiments, the fastener and the force sensor are fixed by integral molding, screwing, interference fitting or bonding, which can ensure that the fastener and the force sensor are rigidly connected as a whole, and ensure that the constraint force generated by the baffle is effectively transmitted to the force sensor.

[0028] In some embodiments, the fastener and the through hole are clearance-fitted to prevent excessive friction caused by interference fit from affecting the detection accuracy of the sensitive component, and to provide suitable clearance space for the elastic deformation of the baffle when the fastener is inserted into the through hole.

[0029] In some embodiments, the at least one fastener includes a plurality of fasteners spaced apart in the circumferential direction to form a circumferential multi-point constraint, which together restricts the rotational degree of freedom of the force sensor, improves the anti-rotation capability of the force sensor when subjected to tangential impact, and prevents the connection between the transmission pin and the wiring harness from loosening due to torsion.

[0030] In some embodiments, the force sensor further includes: a plurality of transmission pins, insulatedly fixed to the main body, the transmission pins being used to electrically connect the internal electrical components of the force sensor to an external wiring harness; wherein the transmission pins are fixed to the main body by integral injection molding, interference fit, welding or bonding.

[0031] Transmission pins are used to enable electrical communication between the internal electrical components (such as the sensing element) of the force sensor and the external wiring harness, thereby enhancing the reliability of the electrical connection.

[0032] According to another aspect of this application, an electromechanical braking device is provided, which is configured with a brake as described in any of the above embodiments.

[0033] By utilizing the brake's fasteners, the electromechanical braking device enables tool-free and rapid installation of the force sensor during assembly and maintains the stability of the force sensor during dynamic braking. This allows the electronic control unit to obtain high-precision braking force feedback through the force sensor, thereby achieving accurate braking control.

[0034] It should be understood that the above general description and the following detailed description are exemplary and explanatory only, and do not limit this application. Attached Figure Description

[0035] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. It is obvious that the drawings described below are merely some embodiments of this application, and those skilled in the art can obtain other drawings based on these drawings without any inventive effort.

[0036] Figure 1 This is a partial structural schematic diagram of the brake provided in an embodiment of this application; Figure 2 A cross-sectional view of the clamp body and force sensor of the brake provided in an embodiment of this application; Figure 3 for Figure 2 A magnified structural diagram of region A in the middle; Figure 4 This is a schematic cross-sectional view of the brake provided in an embodiment of this application; Figure 5 An exploded view of the clamp body and force sensor of the brake provided in the embodiments of this application; Figure 6 This is a schematic diagram of the force sensor provided in an embodiment of this application. Detailed Implementation

[0037] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to those described herein. Rather, these embodiments are provided to make this application more comprehensive and complete, and to fully convey the concept of the exemplary embodiments to those skilled in the art.

[0038] The accompanying drawings are merely illustrative of this application and are not necessarily drawn to scale. The same reference numerals in the drawings denote the same or similar parts, and therefore, repeated descriptions of them will be omitted.

[0039] The use of terms such as "first," "second," and similar words in the specific description does not indicate any order, quantity, or importance, but is merely used to distinguish different components. The term "multiple" means two or more, unless otherwise explicitly specified. Furthermore, in the description of this application, unless otherwise explicitly specified and limited, the term "connection" should be interpreted broadly, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be a connection within two elements.

[0040] It should be noted that, unless otherwise specified, the embodiments of this application and the features in different embodiments can be combined with each other. All other embodiments obtained by those skilled in the art based on the embodiments of this application without inventive effort are within the scope of protection of this application.

[0041] Figure 1 The partial structure of the brake is shown in the diagram. Figure 2 The diagram illustrates the cross-sectional structure of the brake clamp and force sensor. Figure 3 Indicate Figure 2 The magnified structure of region A in the middle, Figure 4 The diagram shows the overall cross-sectional structure of the brake. Figure 5 The diagram illustrates the disassembled structure of the brake's clamp and force sensor. Figure 6 This diagram illustrates the structure of the power sensor, combined with... Figures 1 to 6As shown, the brake provided in this embodiment may include: a caliper body 100, a lead screw assembly 150 assembled in the caliper body 100, a drive motor, and a brake block. The drive motor is located on the power input side 100a of the caliper body 100 and is connected to the lead screw assembly 150 via a transmission component 160 such as a gear. The brake block is located on the power output side 100b of the caliper body 100, and is not specifically shown in the figure.

[0042] The clamp body 100 has a stepped end 101 that protrudes axially toward the lead screw assembly 150. The lead screw assembly 150 includes a lead screw shaft and a lead screw nut. A first component 151 of the lead screw shaft and the lead screw nut passes through the stepped end 101 and is connected to a drive motor, and a second component 152 cooperates with a brake block. The stepped end 101 supports the first component 151 via a first bearing 102.

[0043] The brake also includes: a force sensor 200, comprising an annular main body 210, an outer peripheral wall 220 located on the outer periphery of the main body 210, and a sensitive component (not specifically shown in the figure) disposed in the main body 210 and connected to the outer peripheral wall 220, wherein the main body 210 is disposed between the step end 101 and the first component 151, and the outer peripheral wall 220 is axially pressed against the step end 101 and the first component 151; and At least one fastener 280 is disposed in the main body 210 and extends axially into the through hole 104 of the clamp body 100, wherein the outer periphery of the fastener 280 is provided with a plurality of baffles (281, 282) that are axially distributed and cooperate with the through hole 104.

[0044] The stepped end 101 of the clamp body 100 provides rigid support for the force sensor 200, stably guiding the axial reaction force from the lead screw assembly 150 to the clamp body 100. The lead screw assembly 150 utilizes the first component 151 and the second component 152 to achieve efficient conversion of driving torque into braking thrust. The force sensor 200 is positioned on the transmission path of the braking reaction force. During braking, the braking reaction force on the first component 151 is transmitted to the stepped end 101 through the outer peripheral wall 220, or in other words, the stepped end 101 and the first component 151 jointly apply the load to the outer peripheral wall 220. The outer peripheral wall 220 axially presses against the stepped end 101 of the clamp body 100 and the first component 151 (rotating component) of the lead screw assembly 150, ensuring that the braking reaction force can be accurately transmitted to the sensitive component of the force sensor 200 via the outer peripheral wall 220, guaranteeing the accuracy of force value sensing. The sensitive component refers to the sensing element inside the force sensor 200 that can sense mechanical deformation and convert it into a measurable electrical signal (such as a voltage signal), such as a strain gauge, pressure-sensitive element, or piezoelectric element. Axial Z refers to the direction parallel to the rotation axis of the lead screw assembly 150.

[0045] The fastener 280 has a rod-shaped or columnar extension structure. Through the insertion and engagement of the fastener 280 with the through hole 104, the main body 210 of the force sensor 200 is reliably constrained in the axial Z direction by the clamp body 100, preventing it from moving or rotating under braking vibration or impact loads. This ensures that the pressing state of the outer peripheral wall 220 remains stable, thereby ensuring that the force signal output by the sensitive component can accurately and continuously reflect the braking state. Multiple baffles (281, 282) are provided on the fastener 280, forming a multi-level limiting arrangement along the axial direction between the fastener 280 and the through hole 104. Through multi-point abutment, the main body 210 of the force sensor 200 is reliably constrained by the clamp body 100, effectively preventing axial movement and circumferential deflection caused by braking vibration or impact. This ensures that the force sensor 200 always maintains accurate relative positioning, making the detected force signal stable and reliable. Furthermore, unlike rigid fixing methods, the force sensor 200 utilizes the elastic deformation of the baffles (281, 282) to provide a small preload for fixing, preventing excessive assembly stress from being transmitted to the sensitive components of the force sensor 200 and improving the detection accuracy of the force sensor 200. On another front, the self-tightening design formed by the fasteners 280 and the baffles (281, 282) allows the force sensor 200 to be installed simply by axial pressing, simplifying the assembly process, improving production efficiency, and reducing assembly difficulty caused by limited operating space.

[0046] The baffles (281, 282) can be sheet-like, cantilever-like, hook-like, or other structures that protrude radially outward and extend obliquely along the Z-axis, and are provided on the outer surface of the fastener 280. The baffles (281, 282) can elastically deform during installation to pass through the through hole 104, and abut against the end face (104a, 104b) of the through hole 104 after springing back to achieve locking. The number of fasteners 280 is preferably greater than one, and can be configured as multiple fasteners distributed symmetrically or asymmetrically according to the internal space layout of the caliper.

[0047] During braking, the drive motor responds to the braking command and outputs rotational torque, causing the first component 151 of the lead screw assembly 150 to rotate synchronously. Under the helical transmission between the lead screw shaft and the lead screw nut, the rotational motion of the first component 151 is converted into the linear pushing motion of the second component 152 along the axial direction Z towards the brake block, thereby pressing the brake block against the brake disc and generating a braking clamping force. During this process, the braking reaction force is transmitted to the first component 151 via the brake block and the second component 152. Since the outer peripheral wall 220 of the force sensor 200 is axially pressed between the first component 151 and the step end 101, the braking reaction force is transmitted to the outer peripheral wall 220 of the force sensor 200 in real time and directly. The outer peripheral wall 220, as a rigid force transmission path, accurately transmits the axial load it bears to the sensitive component connected to it; after the sensitive component senses the micro-elastic deformation of the outer peripheral wall 220, it converts the physical force value into a corresponding electrical signal and outputs it to an external controller, thereby realizing the accurate monitoring of the braking force value. Meanwhile, since the fastener 280 is connected to the main body 210 of the force sensor 200 and passes through the through hole 104 of the clamp body 100, the fastener 280 continuously applies a small preload during the entire braking process. This ensures that the detection accuracy of the sensitive component is not affected by excessive preload, and effectively suppresses the movement and displacement of the force sensor 200 caused by mechanical vibration, impact load, etc., so as to ensure that the force sensor 200 is always in a stable and correct sensing position, and to guarantee the accuracy and reliability of the force signal.

[0048] In some embodiments, the plurality of baffles (281, 282) include at least one first baffle 281 and at least one second baffle 282 that extend obliquely toward and away from the main body portion 210, respectively, and one first baffle 281 and one second baffle 282 abut against two opposite end faces (104a, 104b) of the through hole 104 in the axial Z direction.

[0049] During braking, the fastener 280 uses the bidirectional constraint of the first baffle 281 and the second baffle 282 to continuously apply a small bidirectional preload in the axial direction. This will not affect the detection accuracy of the sensitive component due to excessive preload, and will effectively suppress the movement and displacement of the force sensor 200 caused by mechanical vibration, impact load, etc., ensuring that the force sensor 200 is always in a stable and correct sensing position, and guaranteeing the accuracy and reliability of the force signal.

[0050] In some embodiments, both the first baffle 281 and the second baffle 282 are annular and have an outer diameter larger than the inner diameter of the through hole 104, wherein: the first baffle 281 is located at the distal end of the fastener 280 and extends obliquely from the outer periphery of the fastener 280 toward the body portion 210, and the first baffle 281 is used to abut axially against the distal end face 104a of the through hole 104 away from the force sensor 200; the second baffle 282 is located at the proximal end of the fastener 280 and extends obliquely from the outer periphery of the fastener 280 away from the body portion 210, and the second baffle 282 is used to abut axially against the proximal end face 104b of the through hole 104 near the force sensor 200.

[0051] The proximal end refers to the end closer to the force sensor 200 along the Z-axis, while the distal end refers to the end further away from the force sensor 200 and closer to the clamp body 100 along the Z-axis. The baffles (281, 282) are annular, providing a continuous circumferential contact surface to prevent radial sway or tilting of the fastener 280 within the through-hole 104, ensuring the force sensor 200 remains stable under asymmetrical lateral forces. The outer diameter of the baffles (281, 282) is larger than the inner diameter of the through-hole 104, ensuring that the baffles (281, 282) can abut against the end faces (104a, 104b) of the through-hole 104, generating axial preload.

[0052] Furthermore, by utilizing the design that the first baffle 281 is located at the distal end of the fastener 280 and extends obliquely from the outer peripheral surface of the fastener 280 toward the main body 210, and the second baffle 282 is located at the proximal end of the fastener 280 and extends obliquely from the outer peripheral surface of the fastener 280 away from the main body 210, during the installation phase of the force sensor 200, the oblique direction of the first baffle 281 follows the direction in which the fastener 280 extends into the through hole 104, thus acting as a guide cone and reducing the resistance to extending into the through hole 104. After installation, the oblique direction of the first baffle 281 forms a barb structure to prevent the force sensor 200 from coming out. If the force sensor 200 is subjected to an axial force that causes it to come out, the first baffle 281 will have a tendency to expand radially, thereby more tightly fitting the distal end face 104a of the through hole 104 and providing a reliable anti-loosening force. After installation, the second baffle 282 abuts against the proximal end face 104b of the through hole 104. Its elastic deformation not only provides axial pressing preload, but also absorbs the small vibrations of the clamp body 100, preventing vibration energy from being directly transmitted to sensitive components.

[0053] The annular structure of the first baffle 281 and the second baffle 282 can be a complete closed ring or a non-closed ring with stress-relieving grooves. In some applications, the baffle structure is not limited to annular plates and can also be designed as multiple elastic cantilever structures or barbed structures spaced apart in the circumferential direction of the fastener 280. The inclined extension profile of the baffles (281, 282) can be a straight conical surface or an arc-shaped curved surface.

[0054] In some embodiments, the outer diameter of the second baffle 282 is larger than the outer diameter of the first baffle 281, and the number of second baffles 282 is one, while the number of first baffles 281 is multiple.

[0055] The second baffle 282 is located at the proximal end and does not need to pass through the through hole 104 during assembly. Its larger outer diameter provides a larger bearing area, allowing it to firmly abut against the proximal end face 104b of the through hole 104 and preventing it from sinking into the through hole 104. The first baffle 281 is located at the distal end and needs to pass through the through hole 104. Its smaller outer diameter ensures that the compression of the first baffle 281 by the inner wall of the through hole 104 is moderate, facilitating installation and allowing the first baffle 281 to rebound smoothly to abut against the distal end face 104a of the through hole 104. Multiple first baffles 281 (e.g., two to four) can form a redundant locking structure in the circumferential direction, improving the reliability of preventing loosening. The multiple first baffles 281 can be equidistantly distributed along the axial direction or unequally distributed along the axial direction to match different through hole depths.

[0056] In some embodiments, both the first baffle 281 and the second baffle 282 are elastic baffles, capable of undergoing recoverable bending or compressive deformation when subjected to external force, and returning to their initial shape or near-initial shape after the external force is removed, thereby achieving low assembly stress, self-locking, and vibration compensation functions. Specifically, since the baffles (281, 282) are elastic, they can undergo radial contraction (or bending deformation) when passing through the through hole 104, allowing the fastener 280 to slide into the installation position with minimal axial thrust; after passing through the through hole 104, the baffles (281, 282) rely on their stored elastic potential energy to return to their initial state and automatically engage with the end faces (104a, 104b) of the through hole 104. Furthermore, after installation, the baffles (281, 282) act like spring washers, capable of compensating for minute gaps between the clamp body 100 and the fastener 280 caused by vibration, temperature changes, etc., continuously maintaining the axial preload without attenuation, and preventing noise and signal abnormalities caused by loosening.

[0057] Among them, the baffles (281, 282) can be made of metal materials (such as steel sheets, spring steel, etc.), or engineering plastics with a certain rigidity (such as polyether ether ketone, reinforced nylon, etc.), or can adopt a structure in which a metal skeleton is covered with an elastomer material.

[0058] In some embodiments, the first baffle 281 and the second baffle 282 are tilted at an angle α relative to the radial direction of 30° to 60°.

[0059] If the tilt angle α is greater than 60°, the baffles (281, 282) will fit too closely to the outer periphery of the fastener 280. Under axial pull-out force, the baffles (281, 282) are prone to flipping or slipping, leading to locking failure. If the tilt angle α is less than 30°, the baffles will be greatly compressed when inserted into the through hole 104, making installation difficult and potentially scratching the inner wall of the through hole 104 or causing the baffles to break during insertion. Furthermore, it is difficult to achieve axial bidirectional pre-tightening after installation. Limiting the tilt angle α to the range of 30° to 60° ensures both ease of installation and a stable axial bidirectional self-locking mechanism after the baffles (281, 282) spring back.

[0060] In some preferred embodiments, the tilt angle of the baffles (281, 282) is, for example, 40° to 50°, but is not limited thereto. The tilt angle of the first baffle 281 and the tilt angle of the second baffle 282 can be designed to be different values, for example, the tilt angle of the first baffle 281 is larger and the tilt angle of the second baffle 282 is smaller, but is not limited thereto.

[0061] In some embodiments, at least one end face (104a, 104b) of the through hole 104 is provided with a recessed fitting structure, which is adapted to abut against the inclined surface of the corresponding baffle (281, 282) to form axial and radial limiting on the corresponding baffle (281, 282).

[0062] The recessed fitting structure can be exemplified by a conical recess formed by the chamfer of the end faces (104a, 104b) of the through hole 104, a stepped recess formed by the countersunk hole of the end faces (104a, 104b) of the through hole 104, or an annular groove structure formed at the junction of the inner wall of the through hole 104 and the end faces (104a, 104b). The recessed fitting structure provides a mating surface with a geometrically compatible shape for the inclined surfaces of the baffles (281, 282). When the baffles (281, 282) abut against the recessed fitting structure under their own elastic restoring force, the inclined angle or stepped plane of the recessed fitting structure forms a better fit with the inclined surfaces of the baffles (281, 282), preventing the baffles (281, 282) from undergoing plastic deformation or fatigue fracture due to excessive local stress, improving the ability to resist axial dislodgement, and driving the fastener 280 toward the central axis of the through hole 104. The concave-convex structure provides axial and radial limiting for the baffles (281, 282), which also resists vibration and impact loads during brake operation and effectively suppresses the shaking of the fastener 280. This ensures that the axial pressing state between the outer peripheral wall 220 of the force sensor 200 and the first component 151 of the lead screw assembly 150 and the stepped end 101 of the clamp body 100 remains constant, and the force transmission path is accurate, so that the force value sensed by the sensitive component can truly reflect the actual braking force.

[0063] In some embodiments, the fastener 280 and the force sensor 200 are fixed together by integral molding, screwing, interference fitting or bonding.

[0064] By integral molding, the fastener 280 and the main body 210 of the force sensor 200 are rigidly integrated. This integral molding can be achieved using a special demolding structure, simplifying the process. The screw connection is detachable, facilitating the replacement of damaged fasteners 280; the interference fit provides high strength with no risk of loosening; the adhesive process ensures uniform stress distribution and allows the use of insulating and thermally conductive adhesive for both insulation and heat conduction. All of these methods ensure a rigid connection between the fastener 280 and the force sensor 200, guaranteeing that the constraint force generated by the baffles (281, 282) is effectively transmitted to the force sensor 200.

[0065] In some embodiments, the fastener 280 and the through hole 104 are clearance-fitted to prevent excessive friction caused by the interference fit from affecting the detection accuracy of the sensitive component, and to provide suitable clearance space for the elastic deformation of the baffle when the fastener 280 extends into the through hole 104. At the same time, the small gap allows the force sensor 200 to perform a small amount of radial self-alignment under the adjustment of the elastic preload of the baffles (281, 282), ensuring that the force sensor 200 is installed in an accurate position.

[0066] In some embodiments, at least one fastener 280 includes a plurality of fasteners 280 spaced apart in the circumferential direction. The plurality of fasteners 280, such as two or three, form a multi-point constraint in the circumferential direction, which together restricts the rotational degree of freedom of the force sensor 200, improves the anti-rotation capability of the force sensor 200 when subjected to tangential impact, and prevents the connection between the transmission pin and the wiring harness from loosening due to torsion.

[0067] In some embodiments, the force sensor 200 further includes: a plurality of transmission pins 230, which are insulatedly fixed to the main body 210, and the transmission pins 230 are used to electrically connect the internal electrical components of the force sensor 200 to the external wiring harness; wherein the transmission pins 230 and the main body 210 are fixed by integral injection molding, interference fit, welding or bonding.

[0068] The transmission pin 230 is used to establish electrical communication between the internal electrical components (e.g., the sensing element) of the force sensor 200 and the external wiring harness. By fixing the pin, the transmission pin 230 will not transmit stress to the internal electrical components when subjected to tension or vibration from the external wiring harness, thus enhancing the reliability of the electrical connection. The transmission pin 230 is mechanically fixed and electrically isolated from the main body 210 of the force sensor 200 by an insulating component (such as a boss or plate made of glass, ceramic, or plastic) to prevent signal short circuits. The transmission pin 230 can be a rigid pin or a flexible contact. The number of transmission pins 230 can be determined according to the communication protocol used by the force sensor 200 and the electrical functions required by the force sensor 200, for example, including three pins to connect to the power supply harness, grounding harness, and signal harness of the force sensor 200, but is not limited to this.

[0069] In some embodiments, the first component 151 of the lead screw assembly 150 includes two shaft portions with different radial dimensions, wherein: the first shaft portion 151a passes through the stepped end 101 and connects to the drive motor, the second shaft portion 151b cooperates with the second component 152, the stepped end 101 extends axially between the first shaft portion 151a and the second shaft portion 151b; the main body portion 210 is sleeved on the first shaft portion 151a and located between the connecting end face between the first shaft portion 151a and the second shaft portion 151b and the axial end face of the stepped end 101 facing the connecting end face, the outer peripheral wall 220 is pressed against the connecting end face and the axial end face; the main body portion 210 is axially recessed relative to the outer peripheral wall 220, and a sensitive component is used to sense the axial force on the outer peripheral wall 220.

[0070] The first component 151 uses two shafts with different radial dimensions to form an axial force-bearing surface (i.e., a connecting end face). The force sensor 200 is installed between the connecting end face of the first component 151 and the axial end face of the clamp body 100. The transmission path of the braking reaction force is short and the rigidity is high, which helps to achieve accurate detection.

[0071] The main body 210 is axially recessed relative to the outer peripheral wall 220. During installation, the outer peripheral wall 220 serves as the main force boundary, bearing the clamping force between the connecting end face and the axial end face. The recessed main body 210 and its internal sensitive components are in a low-stress zone, which can prevent assembly preload, mechanical impact and overload force from being directly applied to the sensitive components, protecting the sensitive components from high stress damage. This allows the sensitive components to accurately sense the minute axial deformation of the outer peripheral wall 220 caused by the force under low stress conditions and convert the force value into an electrical signal.

[0072] In some embodiments, the first component 151 is a lead screw shaft, and the second component 152 is a lead screw nut. In the lead screw assembly 150, the lead screw shaft is connected to a drive motor and rotates; the lead screw nut is threaded to the lead screw shaft and translates axially. The force sensor 200 is axially pressed between the connecting end face of the lead screw shaft and the axial end face of the clamp body 100.

[0073] Specifically, in combination Figure 3 and Figure 4 As shown, the first shaft portion 151a of the lead screw shaft is a non-threaded section for connecting the drive motor and transmitting torque. The second shaft portion 151b of the lead screw shaft is a threaded portion with internal threads for engaging with the external threads of the lead screw nut to convert rotational motion into linear motion. The large radial dimension of the threaded portion meets the load-bearing strength requirements when engaging with the lead screw nut. The force sensor 200 is sleeved on the first shaft portion 151a. The gap between its inner hole and the first shaft portion 151a not only prevents frictional damage to the force sensor 200 during lead screw shaft rotation but also provides good ventilation and heat dissipation conditions for high-speed rotation of the lead screw shaft, reducing local heat accumulation in the force sensor 200. The main body 210 of the force sensor 200 is axially recessed relative to the outer peripheral wall 220. Under axial compression, the outer peripheral wall 220, as the primary force-bearing boundary, directly bears the clamping force between the axial end face of the step end 101 and the connecting end face of the lead screw shaft. Meanwhile, the recessed main body 210 and its internal sensitive components are located in a low-stress zone, effectively preventing assembly stress and mechanical impact from being directly applied to the sensitive components, thus improving the overload resistance and stability of the force sensor 200. When the outer peripheral wall 220 deforms under axial load, the sensitive components deform accordingly and convert the physical force value into a precise electrical signal. The sensitive components can be any element capable of responding to stress and generating changes in electrical parameters, including but not limited to strain gauges and piezoelectric crystals.

[0074] It should be noted that, although Figure 4 The description focuses on the rotational motion of the lead screw shaft and the translational motion of the lead screw nut, but this application is not limited to this. It can also be implemented where the lead screw nut rotates and the lead screw shaft translates. Specifically, in some embodiments, the first component 151 is the lead screw nut, and the second component 152 is the lead screw shaft. In this case, in the lead screw assembly 150, the lead screw nut is connected to the drive motor and rotates; the lead screw shaft is threadedly engaged with the lead screw nut and translates axially. The force sensor 200 is axially pressed between the connecting end face of the lead screw nut and the axial end face of the clamp body 100. In practical applications, the force transmission path of the lead screw assembly 150 can be configured according to factors such as the drive motor layout, transmission ratio, and wheel-side space requirements. Simply placing the force sensor 200 between the first component 151 and the step end 101 will achieve a direct and definite braking force sensing effect.

[0075] In some embodiments, the outer peripheral wall 220 of the force sensor 200 is pressed against the connecting end face via the second bearing 106; wherein, there may or may not be an axial gap between the outer peripheral wall 220 and the second bearing 106.

[0076] The second bearing 106 allows the rotational freedom of the first component 151 relative to the force sensor 200 to be unrestricted. Simultaneously, it transmits the axial load of the first component 151 to the outer peripheral wall 220 via rolling contact, avoiding frictional torque and wear that might occur from direct contact between the first component 151 and the force sensor 200, thereby minimizing the impact on the detection accuracy of the force sensor 200. A small axial clearance may exist between the outer peripheral wall 220 of the force sensor 200 and the second bearing 106, or there may be no axial clearance or even a slight preload. This eliminates the initial free travel in the braking response and improves the dynamic response speed of braking force detection.

[0077] In some embodiments, the outer peripheral wall 220 is pre-pressed axially between the step end face and the connection end face, specifically between the step end faces of the step end 101 of the second bearing 106. This ensures that the force sensor 200 is subjected to a certain initial pre-pressure in the non-braking state, eliminating assembly gaps and enabling the force sensor 200 to immediately and accurately sense the force signal when braking reaction force is applied. Simultaneously, the pre-pressing also enhances the force sensor 200's vibration and loosening resistance in non-braking conditions, ensuring that the force sensor 200 does not shift when the vehicle is bumpy.

[0078] In some embodiments, the main body 210 is spaced and fitted onto the first shaft 151a, with no direct radial contact between the two. This avoids frictional torque and heat generation between the first shaft 151a and the force sensor 200 during high-speed rotation, preventing thermal drift and wear that could reduce the force measurement accuracy of the force sensor 200 and ensuring the transmission efficiency of the lead screw assembly 150. The spaced fit also prevents the force sensor 200 from being affected by any minor radial runout or bending deformation that may exist in the first shaft 151a. The sensitive component only senses the axial force from the outer peripheral wall 220, ensuring accurate force measurement. The size of the gap can be set according to actual working conditions and is not limited to macroscopically visible dimensions, as long as it ensures that the force sensor 200 is not substantially affected by the radial tension force from the first shaft 151a.

[0079] It should be noted that the lead screw assembly 150 may be a ball screw assembly, but this application is not limited thereto. The lead screw assembly 150 may also be a sliding lead screw mechanism such as a trapezoidal lead screw or a rectangular lead screw, a rolling lead screw mechanism such as a needle roller or a planetary roller, or any other suitable lead screw mechanism.

[0080] This application also provides an electro-mechanical braking system (EMB) configured with a brake as described in any of the above embodiments.

[0081] The electromechanical braking device may include the aforementioned brake and electronic control unit. Using the brake's fastener 280, the force sensor 200 can be quickly and tool-free installed during assembly. During dynamic braking, the force sensor 200 maintains a precise relative position with the caliper body 100 and the lead screw assembly 150, allowing the electronic control unit to obtain high-precision braking force feedback through the force sensor 200, thereby achieving accurate braking control. Furthermore, the vibration and shock resistance of the force sensor 200 ensures the long-term safe and reliable operation of the electromechanical braking device.

[0082] The electromechanical braking device of this application can be applied to various mobile platforms that require high-precision braking control, such as passenger cars, commercial vehicles, or unmanned logistics vehicles.

[0083] In addition to electromechanical braking devices, the brake of this application can also be applied to various braking systems that require precise monitoring of braking force. By utilizing the fastening structure of the force sensor itself, reliable assembly and anti-loosening positioning of the force sensor can be achieved in a compact installation space. Without introducing additional assembly stress or affecting the accuracy of force measurement, it can reliably resist continuous vibration and impact loads during equipment operation, thereby improving the reliability of the braking system.

[0084] Finally, it should be noted that the above description, in conjunction with specific preferred embodiments, provides a further detailed explanation of this application and should not be construed as limiting the specific implementation of this application to these descriptions. For those skilled in the art, various simple deductions or substitutions can be made without departing from the concept of this application, and all such modifications or substitutions should be considered within the scope of protection of this application.

Claims

1. A brake, comprising a clamp body, a lead screw assembly mounted in the clamp body, a drive motor, and a brake block; Its features are, The clamp body has a stepped end that protrudes axially toward the lead screw assembly. The lead screw assembly includes a lead screw shaft and a lead screw nut. A first component of the lead screw shaft and the lead screw nut passes through the stepped end and connects to the drive motor, while a second component engages with the brake block. The stepped end supports the first component via a first bearing. The brake also includes: A force sensor includes an annular main body, an outer peripheral wall located on the outer periphery of the main body, and a sensitive component disposed in the main body and connected to the outer peripheral wall, wherein the main body is disposed between the end of a step and the first component, and the outer peripheral wall axially presses against the space between the end of the step and the first component; and At least one fastener is disposed on the main body and extends axially into the through hole of the clamp body, wherein the outer periphery of the fastener is provided with a plurality of baffles that are axially distributed and cooperate with the through hole; The plurality of baffles includes at least one first baffle and at least one second baffle that extend obliquely toward and away from the main body, respectively, and one first baffle and one second baffle abut against two opposite end faces of the through hole in the axial direction. Both the first and second baffles are annular and have an outer diameter larger than the inner diameter of the through hole. The first baffle is located at the distal end of the fastener and extends obliquely from the outer periphery of the fastener toward the main body. The first baffle is used to abut against the end face of the through hole away from the force sensor in the axial direction. The second baffle is located at the proximal end of the fastener and extends obliquely from the outer periphery of the fastener away from the main body. The second baffle is used to abut against the end face of the through hole near the force sensor in the axial direction.

2. The brake as claimed in claim 1, characterized in that, The outer diameter of the second baffle is larger than the outer diameter of the first baffle. There is one second baffle and multiple first baffles.

3. The brake as described in claim 1, characterized in that, Both the first baffle and the second baffle are elastic baffles; and / or The first baffle and the second baffle are tilted at an angle of 30° to 60° relative to the radial direction.

4. The brake as claimed in claim 1, characterized in that, At least one end face of the through hole is provided with a recessed fitting structure, which is used to abut against the inclined surface of the corresponding baffle to form axial and radial limiting of the corresponding baffle.

5. The brake as claimed in claim 1, characterized in that, The first component includes two shaft portions with different radial dimensions, wherein: The first shaft portion passes through the end of the step and connects to the drive motor, the second shaft portion cooperates with the second component, and the end of the step extends axially between the first shaft portion and the second shaft portion; The main body is sleeved on the first shaft and is located between the connecting end face between the first shaft and the second shaft and the axial end face of the step end facing the connecting end face, and the outer peripheral wall is pressed against the connecting end face and the axial end face. The main body is axially recessed relative to the outer peripheral wall, and the sensitive component is used to sense the axial force on the outer peripheral wall.

6. The brake as claimed in claim 5, characterized in that, The first component is a lead screw shaft, and the second component is a lead screw nut; Alternatively, the first component may be a lead screw nut, and the second component may be a lead screw shaft.

7. The brake as claimed in claim 5, characterized in that, The outer peripheral wall is pressed against the connecting end face via a second bearing; There may or may not be an axial clearance between the outer peripheral wall and the second bearing.

8. The brake as claimed in claim 5, characterized in that, The outer peripheral wall is pre-pressed axially between the axial end face and the connecting end face.

9. The brake as claimed in claim 5, characterized in that, The main body is fitted onto the first shaft portion with a gap.

10. The brake as claimed in claim 1, characterized in that, The fastener is fixed to the force sensor by integral molding, screwing, interference fitting or bonding, and / or the fastener is clearance-fitted to the through hole.

11. The brake as claimed in claim 1, characterized in that, The at least one fastener includes a plurality of fasteners spaced apart in the circumferential direction.

12. The brake as claimed in any one of claims 1 to 11, characterized in that, The force sensor also includes: Multiple transmission pins are insulatedly fixed to the main body, and the transmission pins are used to electrically connect the internal electrical components of the force sensor to an external wiring harness; The transmission pins are fixed to the main body by means of integral injection molding, interference fit, welding or bonding.

13. An electromechanical braking device, characterized in that, The electromechanical braking device is equipped with a brake as described in any one of claims 1 to 12.

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