Floating automotive brake disc

Abstract

The present application relates to a floating automotive brake disc. After the brake disc is assembled, the attachment portion of the friction ring and the first connection portion of the disc cap are connected by hollow pins and solid pins that are circumferentially staggered and evenly distributed. At the same time, fasteners are arranged inside the hollow pins, and both ends of the fasteners pass through the connection holes of the pressure plate and the axial through holes of the second connection portion for locking. After locking, there is a gap between the attachment portion and the pressure plate or the second connection portion, so that only the degree of freedom perpendicular to the friction surface remains among the six degrees of freedom of the friction ring, thereby allowing the friction ring to slightly swing relative to the disc cap in the direction perpendicular to the friction surface, and then automatically centering when the caliper applies force, so as to compensate for the possible position offset of the aluminum-ceramic brake disc due to expansion or thermal deformation, reduce the interference risk, and improve the braking effect and driving safety.

Description

Technical Field

[0001] The present invention relates to the technical field of brake discs, and particularly to a floating automotive brake disc. Background Art

[0002] The ceramic reinforced aluminum matrix composite brake disc, hereinafter referred to as the aluminum-ceramic disc, has become an ideal substitute for traditional steel brake discs due to its advantages such as light weight, good thermal conductivity, and strong corrosion resistance, and has broad application prospects in the field of rail transit and new energy vehicles. However, the aluminum-ceramic brake disc still faces some technical challenges in practical applications. For example, compared with cast iron materials and carbon-ceramic materials, the ceramic reinforced aluminum matrix composite has a relatively large coefficient of thermal expansion. Therefore, during repeated braking, the aluminum-ceramic brake disc may undergo irreversible thermal deformation, especially under high temperature and uneven temperature conditions. For traditional split aluminum-ceramic brake discs, the friction ring and the disc cap are usually axially locked, and there is not enough space allowance to eliminate the axial load caused by thermal deformation. This may lead to the offset of the friction ring position and the decline of friction performance. At the same time, it may also cause interference to other surrounding components, such as calipers, thus affecting driving safety and braking effect. Summary of the Invention

[0003] Based on this, it is necessary to provide a floating automotive brake disc, in which there is enough space allowance between the disc cap and the friction ring to eliminate the axial load caused by thermal deformation, thereby improving driving safety and braking effect.

[0004] A floating automotive brake disc, comprising:

[0005] A disc cap, the disc cap includes a cap body and a first connecting portion and a second connecting portion extending radially outward along the cap body. The outer diameter of the first connecting portion is smaller than that of the second connecting portion. The first connecting portion is evenly distributed with first grooves along the outer circumference, and the second connecting portion is provided with axial through holes at several first groove positions in a circumferentially evenly distributed manner;

[0006] A friction ring coaxially arranged with the disc cap, the friction ring includes a disc body and an attachment portion extending radially inward along the disc body. The attachment portion is evenly distributed with second grooves along the inner circumference, which have the same number and corresponding positions as the first grooves. The first groove at the position where the axial through hole is provided and the corresponding second groove enclose a hollow pin accommodating space, and the first groove at the position where no axial through hole is provided and the corresponding second groove enclose a solid pin accommodating space;

[0007] A pressing plate covering the hollow pin accommodating space and the solid pin accommodating space, and the pressing plate is provided with connecting holes having the same number and corresponding positions as the axial through holes;

[0008] Hollow pins having the same number and shape matching as the hollow pin receiving spaces, each of the hollow pins being disposed in a corresponding hollow pin receiving space;

[0009] Solid pins having the same number and shape matching as the solid pin receiving spaces, each of the solid pins being disposed in a corresponding solid pin receiving space; and

[0010] Fasteners having the same number and shape matching as the hollow pins, each of the fasteners being disposed in a corresponding hollow pin, and passing through a corresponding connection hole and an axial through hole at both ends for locking. After locking, a gap is left between the attachment portion and the pressing plate or the second connecting portion.

[0011] In one embodiment, after locking, the gap is 0.1 mm to 0.5 mm.

[0012] In one embodiment, the second connecting portion is provided with axial through holes at positions corresponding to the first grooves at intervals of at least one first groove.

[0013] In one embodiment, the second connecting portion is provided with axial through holes at positions corresponding to the first grooves at intervals of two first grooves, and the number of the axial through holes is nine.

[0014] In one embodiment, a hollow pin elastic member is disposed in each of the hollow pin receiving spaces for elastically supporting the hollow pin.

[0015] In one embodiment, the elastic force of the hollow pin elastic member can support 2 to 10 times the self-weight of the hollow pin.

[0016] In one embodiment, a solid pin elastic member is further disposed in each of the solid pin receiving spaces for elastically supporting the solid pin.

[0017] In one embodiment, the elastic force of the solid pin elastic member can support 2 to 10 times the self-weight of the solid pin.

[0018] In one embodiment, each of the hollow pins is in close circumferential fit with a corresponding hollow pin receiving space; each of the solid pins is in close circumferential fit with a corresponding solid pin receiving space.

[0019] In one embodiment, after locking, the distance between the radially inner edge of the pressing plate and the radially outer edge of the cap body is 0.3 mm to 0.8 mm, and the distance between the radially outer edge of the pressing plate and the radially inner edge of the disc body is 0.3 mm to 0.8 mm.

[0020] After the above floating automotive brake disc is assembled, the attachment part of the friction ring and the first connection part of the disc cap are connected by hollow pins and solid pins that are circumferentially staggered and evenly distributed. At the same time, fasteners are arranged inside the hollow pins, and both ends of the fasteners pass through the connection holes of the pressing plate and the axial through holes of the second connection part to be locked. After locking, there is a gap between the attachment part and the pressing plate or the second connection part, so that only the degree of freedom perpendicular to the friction surface is retained among the six degrees of freedom of the friction ring, thereby allowing the friction ring to slightly swing relative to the disc cap in the direction perpendicular to the friction surface, and then automatically centering when the caliper applies force to compensate for the possible position offset of the aluminum-ceramic brake disc due to expansion or thermal deformation, reduce the interference risk, and improve the braking effect and driving safety.

[0021] In addition, by arranging solid pins in the solid pin accommodation space, the connection strength between the friction ring and the disc cap can be improved. Brief Description of the Drawings

[0022] Figure 1 is a schematic structural diagram of a floating automotive brake disc according to an embodiment;

[0023] Figure 2 is Figure 1 a cross-sectional view of the floating automotive brake disc in

[0024] Figure 3 is Figure 1 an exploded structural diagram of the floating automotive brake disc in Detailed Embodiment

[0025] To facilitate the understanding of the present invention, the present invention will be described more comprehensively below, and preferred embodiments of the present invention are given. However, the present invention can be implemented in many different forms and is not limited to the embodiments described herein. On the contrary, the purpose of providing these embodiments is to make the understanding of the disclosure content of the present invention more thorough and comprehensive.

[0026] It should be noted that when an element is referred to as being "disposed" on another element, it can be directly on the other element or there can also be an intermediate element.

[0027] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those of ordinary skill in the technical field to which the present invention belongs. The terms used herein in the specification of the present invention are only for the purpose of describing specific embodiments and are not intended to limit the present invention. The term "and / or" used herein includes any and all combinations of one or more of the related listed items.

[0028] Please refer to Figures 1 to 3 , a floating automotive brake disc 10 according to an embodiment includes a disc cap 11, a friction ring 13, a pressing plate 15, a hollow pin 17, a solid pin 18, and a fastener 19.

[0029] Among them, the disc cap 11 includes a cap body 111, a first connecting portion 113 and a second connecting portion 115 that extend radially outward along the cap body 111. The outer diameter of the first connecting portion 113 is < the outer diameter of the second connecting portion 115. The first connecting portion 111 is provided with first grooves (not marked in the figure) evenly distributed along the outer circumference. The second connecting portion 115 is provided with axial through holes 117 at several first groove positions in a circumferentially evenly distributed manner.

[0030] It should be noted that the second connecting portion 115 is provided with axial through holes 117 at several first groove positions in a circumferentially evenly distributed manner, which means that the second connecting portion 115 can be provided with axial through holes 117 at each first groove position, or can be provided with axial through holes 117 at corresponding first groove positions in a manner of every n first grooves, where n≥1.

[0031] In this embodiment, the second connecting portion 115 is provided with axial through holes 117 at corresponding first groove positions in a manner of at least every two first grooves.

[0032] Furthermore, the second connecting portion 115 is provided with axial through holes 117 at corresponding first groove positions in a manner of every two first grooves, and the number of the axial through holes 117 is 9.

[0033] The above arrangement of the axial through holes 117 can effectively improve the structural stability of the brake disc 10 and the ability to transmit torque, and while avoiding the reduction of the strength or deformation of the second connecting portion 115, it realizes the balanced force and automatic centering between the friction ring 13 and the disc cap 11.

[0034] The friction ring 13 is coaxially arranged with the disc cap 11.

[0035] Among them, the friction ring 13 includes a disc body 131 and an attachment portion 133 that extends radially inward along the disc body 131. The attachment portion 133 is provided with second grooves evenly distributed along the inner circumference and having the same number and corresponding positions as the first grooves.

[0036] It can be understood that the upper and lower surfaces of the disc body 131 are the friction surfaces.

[0037] The first groove at the position where the axial through hole 117 is provided and the corresponding second groove enclose a hollow pin accommodation space. The first groove at the position where the axial through hole 117 is not provided and the corresponding second groove enclose a solid pin accommodation space.

[0038] In this embodiment, the hollow pin accommodation space is used to accommodate the hollow pin 17. Therefore, the hollow pin 17 has the same number and matching shape as the hollow pin accommodation space. After assembly, each hollow pin 17 is arranged in the corresponding hollow pin accommodation space and is tightly fitted with the corresponding hollow pin accommodation space in the circumferential direction for transmitting the braking torque.

[0039] In this embodiment, the solid pin accommodation space is used to accommodate the solid pin 18. Therefore, the number of solid pins 18 is the same as that of the solid pin accommodation spaces, and their shapes match. After assembly, each solid pin 18 is disposed in the corresponding solid pin accommodation space and is in close fit with the corresponding solid pin accommodation space in the circumferential direction for transmitting the braking torque.

[0040] It can be understood that if the second connecting portion 115 is provided with an axial through hole 117 at each first groove position, there will be no solid pin accommodation space, and naturally there will be no corresponding solid pin.

[0041] The pressure plate 15 is used to cover the above-mentioned hollow pin accommodation space and solid pin accommodation space. The pressure plate 15 is provided with connecting holes 151 having the same number and corresponding positions as the axial through holes 117.

[0042] The number of fasteners 19 is the same as that of the hollow pins 17 and their shapes match. After assembly, each fastener 19 is disposed in the corresponding hollow pin 17, and both ends respectively pass through the corresponding connecting holes 151 and axial through holes 117 for locking. After locking, there is a gap between the attachment portion 133 and the pressure plate 15 or the second connecting portion 115.

[0043] By setting the gap, the friction ring 13 can have a certain degree of freedom in the direction perpendicular to the friction surface, so as to automatically center when the caliper applies force, to compensate for the possible position offset of the aluminum ceramic brake disc due to expansion or thermal deformation, reduce the interference risk, and improve the braking effect and driving safety. At the same time, it can also prevent external media from infiltrating into the hollow pin accommodation space and solid pin accommodation space and affecting the damping effect and the automatic centering performance of the friction ring 13.

[0044] Furthermore, the gap is 0.1 mm to 0.5 mm. That is, after assembly and locking, the distance between the attachment portion 133 and the pressure plate 15 or the second connecting portion 115 is 0.1 mm to 0.5 mm. If the gap is too small, it will increase the drag force and thermal expansion between the friction ring 13 and the disc cap 11, resulting in noise and wear; if the gap is too large, it will affect the braking response time and braking force, and even lead to brake failure.

[0045] In this embodiment, the fastener 19 includes a bolt 191 and a nut 193. After assembly, the bolt 191 penetrates from the connecting hole 151, passes through the hollow pin 17 and the axial through hole 117 in sequence, and is locked with the nut 193.

[0046] Further, after locking, the distance between the radially inner edge of the pressing plate 15 and the radially outer edge of the cap body 111 is 0.3 mm to 0.8 mm, and the distance between the radially outer edge of the pressing plate 15 and the radially inner edge of the disc body 131 is 0.3 mm to 0.8 mm. On the one hand, it facilitates the slight swing of the friction ring 13 in the direction perpendicular to the friction surface, and on the other hand, it can effectively prevent the pressing plate 15 from interfering or colliding with the cap body 111 or the disc body 111 due to thermal expansion during braking, thereby avoiding the generation of noise or damage.

[0047] In this embodiment, a hollow pin elastic member 171 is further provided in each hollow pin accommodation space, and the elastic force of the hollow pin elastic member 171 can support 2 to 10 times the self-weight of the hollow pin 17.

[0048] In this embodiment, a solid pin elastic member 181 is further provided in each solid pin accommodation space, and the elastic force of the solid pin elastic member 181 can support 2 to 10 times the self-weight of the solid pin 18.

[0049] The above settings of the hollow pin elastic member 171 and the solid pin elastic member 181 are used, on the one hand, to elastically support the hollow pin 17 and the solid pin 18, so that only the degree of freedom perpendicular to the friction surface of the six degrees of freedom of the friction ring 13 is retained, thereby allowing the friction ring 13 to slightly swing relative to the disc cap 11 in the direction perpendicular to the friction surface, and then automatically centering when the caliper applies force to compensate for the possible position offset caused by the expansion or thermal deformation of the aluminum-ceramic brake disc, reducing the interference risk, and improving the braking effect and driving safety; on the other hand, it can prevent the hollow pin 17 and the solid pin 18 from deforming or loosening during installation, and improve the connection strength and stability between the friction ring 13 and the disc cap 11. At the same time, the settings of the hollow pin elastic member 171 and the solid pin elastic member 181 can also buffer vibration and shock, and reduce noise and wear.

[0050] In this embodiment, both the hollow pin elastic member 171 and the solid pin elastic member 181 are springs.

[0051] For the above floating automotive brake disc 10, after assembly, the attachment portion 133 of the friction ring 13 and the first connection portion 113 of the disc cap 11 are connected by circumferentially staggered and evenly distributed hollow pins 17 and solid pins 18. At the same time, a fastener 19 is arranged inside the hollow pin 17, and both ends of the fastener 19 pass through the connection hole 151 and the axial through hole 117 and are locked, so that only the degree of freedom perpendicular to the friction surface of the six degrees of freedom of the friction ring 13 is retained, thereby allowing the friction ring 13 to slightly swing relative to the disc cap 11 in the direction perpendicular to the friction surface, and then automatically centering when the caliper applies force to compensate for the possible position offset caused by the expansion or thermal deformation of the aluminum-ceramic brake disc, reducing the interference risk, and improving the braking effect and driving safety.

[0052] In addition, the accommodation space formed by enclosing the first groove and the second groove can form a relatively airtight space through the cooperation of the pressing plate 15 and the fastener 19, which can effectively prevent the inflow of external media and prevent the damping in the cavity from being affected due to excessive infiltration of external media, thereby affecting the automatic centering of the friction ring and causing problems such as chucking and eccentricity.

[0053] The above-described embodiments merely represent several implementation manners of the present invention, and the description thereof is relatively specific and detailed. However, it should not be construed as a limitation to the scope of the patent of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present invention, several modifications and improvements can still be made, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the patent of the present invention shall be subject to the appended claims.

Claims

1. A floating automotive brake disc, characterized in that, Comprising: A disc cap, the disc cap includes a cap body, a first connecting portion and a second connecting portion that extend radially outward along the cap body. The outer diameter of the first connecting portion is smaller than that of the second connecting portion. The first connecting portion is circumferentially provided with first grooves on the outer side. The second connecting portion is provided with axial through holes at several first groove positions in a circumferentially distributed manner; A friction ring coaxially arranged with the disc cap, the friction ring includes a disc body and an attachment portion that extends radially inward along the disc body. The attachment portion is circumferentially provided with second grooves having the same number and corresponding positions as the first grooves. The first groove at the position where the axial through hole is provided and the corresponding second groove enclose a hollow pin accommodating space. The first groove at the position where no axial through hole is provided and the corresponding second groove enclose a solid pin accommodating space; A pressing plate covering the hollow pin accommodating space and the solid pin accommodating space, and the pressing plate is provided with connecting holes having the same number and corresponding positions as the axial through holes; Hollow pins having the same number and shape matching as the hollow pin accommodating spaces, and each hollow pin is arranged in a corresponding hollow pin accommodating space; Solid pins having the same number and shape matching as the solid pin accommodating spaces, and each solid pin is arranged in a corresponding solid pin accommodating space; And Fasteners having the same number and shape matching as the hollow pins, and each fastener is arranged in a corresponding hollow pin, and both ends respectively pass through the corresponding connecting holes and axial through holes for locking. After locking, there is a gap between the attachment portion and the pressing plate or the second connecting portion.

2. The floating automotive brake disc according to claim 1, wherein After locking, the gap is 0.1 mm to 0.5 mm.

3. The floating automotive brake disc according to claim 1, wherein The second connecting portion is provided with axial through holes at corresponding first groove positions in a manner of at least one first groove interval.

4. The floating automotive brake disc according to claim 3, wherein, The second connecting portion is provided with axial through holes at corresponding first groove positions in a manner of two first groove intervals, and the number of the axial through holes is nine.

5. The floating automotive brake disc according to claim 1, wherein, Each hollow pin accommodating space is further provided with a hollow pin elastic member for elastically supporting the hollow pin.

6. The floating automotive brake disc according to claim 5, characterized in that, The elastic force of the hollow pin elastic member can support 2 to 10 times the self-weight of the hollow pin.

7. The floating automotive brake disc according to claim 1, characterized in that, Each solid pin accommodating space is further provided with a solid pin elastic member for elastically supporting the solid pin.

8. The floating automotive brake disc according to claim 7, wherein, The elastic force of the solid pin elastic member can support 2 to 10 times the self-weight of the solid pin.

9. The floating automotive brake disc according to claim 1, wherein Each hollow pin is in close fit with the corresponding hollow pin accommodating space in the circumferential direction; each solid pin is in close fit with the corresponding solid pin accommodating space in the circumferential direction.

10. The floating automotive brake disc according to claim 1, characterized in that, After locking, the distance between the radially inner edge of the pressing plate and the radially outer edge of the cap body is 0.3 mm to 0.8 mm, and the distance between the radially outer edge of the pressing plate and the radially inner edge of the disc body is 0.3 mm to 0.8 mm.

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