CN217177232U

CN217177232U - Disc brake

Info

Publication number: CN217177232U
Application number: CN202122969898.1U
Authority: CN
Inventors: 刘浩然
Original assignee: Bosch Rexroth Beijing Hydraulic Co Ltd
Current assignee: Bosch Rexroth Beijing Hydraulic Co Ltd
Priority date: 2021-11-30
Filing date: 2021-11-30
Publication date: 2022-08-12
Anticipated expiration: 2031-11-30

Abstract

The utility model provides a disc brake, its planetary gear case for vehicle, disc brake (1) include main shaft (11), arrange in brake disc subassembly (12) on the inner wall of main shaft (11) and can extrude piston (13) of outer brake disc (121) in the outside of brake disc subassembly (12), wherein, the court of piston (13) be constructed with piston end lubricating oil passageway (131) on the terminal surface of brake disc subassembly (12), and/or main shaft (11) on the inner wall towards brake disc subassembly (12) is constructed with main shaft end lubricating oil passageway (111).

Description

Disc brake

Technical Field

The utility model relates to a new lubrication design of gear box in the braking field particularly, relates to a disc brake of planetary gear box for vehicle.

Background

The multiple disc brake is an important component in a planetary gearbox, the brake discs of which generate heat as the drive motor rotates. If the rotational speed of the brake disc is high and the number of brake discs is high, the heat generated by the brake discs will be much higher, which will result in a temperature increase and oil deterioration of the gearbox. More importantly, if the heat cannot be discharged in time, the service life of the brake disc can be shortened.

In order to carry away the braking friction energy, the oil inside the gearbox should pass through the brake disc and circulate between the drive motor side and the planet gear side. Several oil passages have been used in the prior art to undertake this task.

However, the disadvantages of the current design are as follows:

1. oil passes from the oil holes through the gap of each brake disc to the input shaft, but the gap is too narrow to allow sufficient oil to pass. If the gearbox speed is high, the oil cannot take away sufficient heat, and the temperature rises;

2. the bearing clearance is too small to allow oil to pass through. Thus, the lubrication on the right side of the brake is poor compared to its left side.

SUMMERY OF THE UTILITY MODEL

According to a different aspect, the technical problem to be solved by the present invention is how to improve the oil lubrication of a disc brake for a planetary gearbox of a vehicle.

Furthermore, the present invention also aims to solve or alleviate other technical problems existing in the prior art.

The utility model discloses a disc brake solves above-mentioned problem, particularly, according to the utility model discloses an aspect provides:

a disc brake, wherein it is for a planetary gearbox of a vehicle, comprising a main shaft, a brake disc assembly arranged on an inner wall of the main shaft and a piston capable of pressing an outer brake disc outside the brake disc assembly, wherein piston end lubrication channels are configured on an end surface of the piston facing the brake disc assembly and/or spindle end lubrication channels are configured on the inner wall of the main shaft facing the brake disc assembly.

Drawings

The above and other features of the present invention will become apparent with reference to the accompanying drawings, in which,

fig. 1 shows a partial cross-sectional view of a disc brake of the present invention;

figure 2 shows a plan partial cross-sectional view of a disc brake of the present invention;

fig. 3 shows a piston end view of a disc brake according to the present invention;

fig. 4 shows a cutaway perspective view of a main shaft of a disc brake of the present invention;

fig. 5 shows a spindle end view of a disc brake according to the present invention;

fig. 6 shows a detail partial view of a main shaft end face of a disc brake of the present invention; and

fig. 7 shows a schematic diagram of an oil circuit of a disc brake according to the present invention.

Detailed Description

It is easily understood that, according to the technical solution of the present invention, a plurality of alternative structural modes and implementation modes can be proposed by those skilled in the art without changing the spirit of the present invention. Therefore, the following detailed description and the accompanying drawings are merely illustrative of the technical solutions of the present invention, and should not be considered as limiting or restricting the technical solutions of the present invention in their entirety or in any other way.

The terms of orientation of up, down, left, right, front, back, top, bottom, and the like referred to or may be referred to in this specification are defined relative to the configuration shown in the drawings, and are relative terms, and thus may be changed correspondingly according to the position and the use state of the device. Therefore, these and other directional terms should not be construed as limiting terms. Furthermore, the terms "first," "second," "third," and the like are used for descriptive and descriptive purposes only and not for purposes of indication or implication as to the relative importance of the respective components.

With reference to fig. 1 and 2, they show a partial section view of a disc brake 1 according to the invention and a partial section view of a plane of a disc brake according to the invention, respectively.

The disc brake 1 is for a planetary gearbox of a vehicle, the disc brake 1 comprising a main shaft 11, a brake disc assembly 12 arranged on an inner wall of the main shaft 11, and a piston 13 capable of pressing an outer brake disc 121 outside the brake disc assembly 12.

It should be understood that the brake disc assembly 12 further has an inner brake disc 122, wherein the outer brake disc 121 and the inner brake disc 122 are stacked in sequence overlapping each other, the outer brake disc 121 is disposed on the main shaft 11, and a specific arrangement may be that an inner wall of the main shaft 11 corresponding to the position of the outer brake disc 121 is configured with a notch 113, and the outer brake disc 121 is inserted into the notch 113 and can move in the notch 113 when being stressed. The inner brake disc 122 is fitted over the input shaft 16 of the disc brake 1 and can be driven by the input shaft 16, the input shaft 16 being connected at one end to a drive motor, so that its movement is driven by the drive motor, and at the other end to the sun gear of the planetary gearbox. During operation of the planetary gearbox, the input shaft 16 rotates the inner brake disc 122. At this time, the piston 13 is separated from the outer disc 121, and thus the outer disc 121 is fixed. There is thus a relative rotation between the outer brake disc 121 and the inner brake disc 122. In the process, brake disk friction is generated, and a large amount of heat energy is generated. As the rotation speed of the driving motor increases and the number of the outer and

inner brake disks

121 and 122 increases, the generated heat energy may further increase. For braking, the piston 13 may be driven by the elastic force of the spring 15 located inside thereof to press the outer brake disc 121, so that the outer brake disc 121 is forced to move in the notch 113 and rub in contact with the inner brake disc 122, so that the inner brake disc 122 prevents the input shaft 16 from rotating, thereby completing the braking of the planetary gearbox. In this connection, the piston 13 can also be referred to as a press structure. The disk brake 1 can also be referred to as a reduction gear, which can be used in various vehicles, such as pure electric vehicles or hybrid vehicles. It will be understood that, even if the pistons 13 do not act on the outer discs 121, the outer discs 121 and the inner discs 122 still generate frictional heat energy when the planetary gearbox is in operation.

Referring to fig. 3, there is shown a piston end view of a disc brake 1 according to the present invention.

A piston end lubricating oil channel 131 is formed on the end face of the piston 13 facing the brake disk assembly 12. It should be understood that the piston end lubrication oil passage 131 is a passage for the flow of lubrication oil. The amount of circulating oil can be increased by the piston end lubricating oil passage 131 while increasing the circulating speed to take more heat energy away. In addition, because the piston end lubricating oil channel 131 is directly constructed on the end surface of the piston 13, no additional parts are needed, so that the technical scheme has better compatibility and adaptability, and cannot influence the matching mode, the occupied space and the like of the existing parts.

Illustratively, the piston-end lubrication oil passage 131 is configured in a groove structure, and the piston-end lubrication oil passage 131 is evenly distributed around the axis of the main shaft 11 on the end surface of the piston 13. It will be appreciated that the design of the groove structure is such that the original pressing action of the piston 13 against the outer brake disc 121 is not affected, since the parts of the end surface of the piston 13 other than the groove structure remain intact. It should also be understood that the axis of the spindle 11 is the central or longitudinal axis of the spindle 11, which extends horizontally in the figures. The uniform distribution achieves uniform distribution and guidance of the flow of the lubricating oil. Optionally, the groove structure is configured as a linear groove structure. By linear groove structure is meant that the longitudinal sides of the groove structure are straight and parallel to each other (which can be seen well in fig. 3), whereby the cross-section of the piston-end lubrication oil channel 131 on the end face of the piston 13 resembles a rectangle. This configuration has the advantage of being simple to manufacture and provides a smooth flow path for the lubricating oil.

Reference is made to fig. 4, 5 and 6, which respectively show a cut-away perspective view of the main shaft of a disc brake according to the present invention; the utility model discloses a main shaft end face diagram of a disc brake; and the utility model discloses a main shaft end surface detail local map of disc brake.

A spindle-end lubricating oil passage 111 is formed on the inner wall of the spindle 11 toward the brake disc assembly 12. Thus, the main shaft end lubrication oil passage 111 provides another way for oil lubrication of the brake disc assembly 12, and particularly, the additional oil passage in the main shaft allows more oil to enter the right side of the brake, thereby preventing heat from being conducted poorly on the right side of the brake. Similar to the piston-end lubrication oil channel 131, since the main shaft-end lubrication oil channel 111 is directly formed on the inner wall of the main shaft 11, no additional parts are required, and thus, the technical solution has good compatibility and adaptability, and does not affect the matching manner of the existing parts, the occupied space, and the like.

As can also be seen in conjunction with fig. 1 and 2, the disc brake 1 further has a bearing 14, the bearing 14 being arranged on the piston-free end side of the brake disc assembly 12 and being mounted on a central inner bore 114 of the main shaft 11 for supporting the input shaft 16, the main shaft 11 having a bearing flange 112 which is fitted on the bearing 14, the main shaft-end lubrication channel 111 comprising a first groove 1111 and a second channel 1112, wherein the first groove 1111 extends on the inner wall in the axial direction of the main shaft 11 towards the outer periphery of the brake disc assembly 12, and the second channel 1112 is formed on the bearing flange 112.

It should be understood that the piston-free end side of the brake disc assembly 12 is the right side of the brake disc assembly 12 in the figures. The bearing flange 112 is located at the right end of the main shaft 11 and is an annular part of minimum radial dimension. The bearing 14 can be fitted to the input shaft 16 in addition to supporting the main shaft 11. The bearing flange 112 is thus also arranged on the piston-free end side of the brake disc assembly 12. The axial direction of the spindle 11, i.e. the direction of the center axis or longitudinal axis of the spindle 11, is horizontal in the figure. The first groove 1111 faces the outer peripheral edge of the brake disc assembly 12 means that the groove bottom of the first groove 1111 and the outer peripheral edge of the brake disc assembly 12 face each other. In addition, it should be noted that the main shaft is a main supporting component, and is fixed on the frame of the customer, and other components are installed on the main shaft, and the main shaft plays a role of supporting the bearing. The input shaft can also be understood as a propeller shaft.

As can be seen from the above solution, the first recess 1111 extends horizontally and is located radially outside the outer circumference of the brake disc assembly 12 so as to transfer heat to the brake disc assembly 12 in the radial direction. While the second channel 1112 can be used for heat transfer to the brake disc assembly 12 on the end face side.

With regard to the specific design of the second channel 1112, it is possible that the second channel 1112 comprises a groove 11121 and a through hole 11122, wherein the groove 11121 is arranged on the end face of the bearing flange 112 facing the brake disk assembly 12, and the through hole 11122 penetrates the bearing flange 112 in the axial direction of the main shaft 11. This solution provides a clear division of the function of the second channels 1112, i.e. the grooves 11121 are mainly used for heat transfer to the brake disc assembly 12 on the end side, while the through-holes 11122 are mainly used for flow guidance of the lubricating oil and are used for heat transfer to the brake disc assembly 12 on the end side. In addition, it should be noted that the term "groove" is meant to be the same as a groove, i.e. it includes the bottom of the groove as well as two sides, but the top is open, without the expression of the top of the groove.

It is also possible that the groove 11121 communicates with the through hole 11122, and the through hole 11122 communicates with the first groove 1111. Thereby, the flow of the lubricating oil is made smoother in these areas, and the efficiency of the heat transfer is improved. A specific way of communication may be that the end of the through hole 11122 facing the brake disc assembly 12 opens into the groove bottom of the groove 11121, but of course, the end of the through hole 11122 only needs to pass through a part of the groove bottom and also communicates with the first groove 1111. The through hole 11122 can thus be regarded as an intermediate part.

As can be seen well in fig. 6, the cross section of the through-opening 11122 at the end face of the bearing flange 112 is configured in the form of a non-closed circle with an opening. It can be seen that the through hole 11122 communicates with the first recess 1111 by this non-closed circular design. The advantage of this design is that the design of direct communication based on the shape characteristics of the through hole 11122 is simple, efficient, does not occupy extra resources, and has good adaptability to the shape of the first groove 1111. Furthermore, the circular configuration is relatively simple to manufacture, easy to use, and also has a good fit to the shape of the first recess 1111.

As can also be seen well in fig. 6, the groove 11121 is configured as a linear groove whose two parallel sides, viewed in the cross-sectional plane of the bearing flange 112, are each tangent to the through-opening 11122. In this context, a "linear groove" is to be read in the same way as the linear groove structure mentioned above, i.e. its longitudinal sides are straight lines parallel to each other, whereby the linear groove resembles, in a cross-sectional plane of the bearing flange 112, a rectangle lacking a short side. This configuration has the advantage of being simple to manufacture and provides a smooth flow path for the lubricating oil. The design reasons for the "tangential" solution are on the one hand simple production and on the other hand the ability to provide as large a flow cross section as possible for the lubricating oil, in order to obtain a large heat transfer surface area.

Further, alternatively, the first groove 1111 and the second channel 1112 are provided in a pair with each other, and the first groove 1111 and the second channel 1112 are evenly distributed around the axis of the main shaft 11. The meaning of the axis of the spindle or the technical effect of the uniform distribution has already been explained above or can be interpreted analogously. The advantage of being paired with each other is ease of manufacture and control over the flow path of the lubricating oil and the effect of heat transfer.

Finally, referring to fig. 7, a schematic diagram of an oil circuit of a disc brake according to the present invention is shown.

The figure depicts with arrows the lubricating oil flow path and the corresponding heat transfer effect that can be achieved thereby by the oil channel design of the disc brake 1 of the present invention. It can be seen that the present application provides additional lubricant flow paths on both end surfaces and the peripheral side of the disc brake 1, which increases the flow rate of lubricant in these areas, helps to take away more heat energy generated by friction of the brake disc, and at the same time increases the circulation rate of lubricant, increases the lubrication rate, and increases the circulation amount of lubricant from the left and right sides of the disc brake 1, thereby increasing the heat exchange efficiency of lubricant, ultimately reducing the temperature of the gear box, increasing the life of the brake disc, and increasing the life of lubricant.

It should be understood that all of the above preferred embodiments are exemplary and not restrictive, and that various modifications and changes in the specific embodiments described above, which may occur to those skilled in the art upon reading the teachings of the present invention, are intended to be within the scope of the appended claims.

Claims

1. Disc brake (1), characterised in that it is for a planetary gearbox of a vehicle, the disc brake (1) comprising a main shaft (11), a brake disc assembly (12) arranged on the inner wall of the main shaft (11) and a piston (13) capable of pressing an outer brake disc (121) outside the brake disc assembly (12), wherein a piston end lubrication channel (131) is configured on the end surface of the piston (13) facing the brake disc assembly (12) and/or a main shaft end lubrication channel (111) is configured on the inner wall of the main shaft (11) facing the brake disc assembly (12).

2. The disc brake (1) according to claim 1, characterized in that the piston-end lubrication oil channel (131) is configured as a groove structure and/or the piston-end lubrication oil channel (131) is evenly distributed around the axis of the main shaft (11) on the end face of the piston (13).

3. The disc brake (1) according to claim 2, characterized in that the groove structure is configured as a linear groove structure.

4. The disc brake (1) according to claim 1, characterized in that it further has a bearing (14), the bearing (14) being arranged on the piston-free end side of the brake disc assembly (12) and being mounted on a central inner bore (114) of the main shaft (11), the main shaft (11) having a bearing flange (112) which is fitted over the bearing (14), the main shaft-end lubrication channel (111) comprising a first groove (1111) and/or a second channel (1112), wherein the first groove (1111) extends on the inner wall radially outside the outer periphery of the brake disc assembly (12) in the axial direction of the main shaft (11), the second channel (1112) being configured on the bearing flange (112).

5. The disc brake (1) according to claim 4, characterized in that the second channel (1112) comprises a groove (11121) and a through hole (11122), wherein the groove (11121) is arranged on an end face of the bearing flange (112) facing the brake disc assembly (12), the through hole (11122) penetrating the bearing flange (112) in the axial direction of the main shaft (11).

6. The disc brake (1) according to claim 5, characterized in that the groove (11121) communicates with the through-hole (11122) and/or the through-hole (11122) communicates with the first groove (1111).

7. The disc brake (1) according to claim 5 or 6, characterized in that the cross section of the through-opening (11122) on the end face of the bearing flange (112) is configured as a non-closed circle with an opening.

8. The disc brake (1) according to claim 6, characterized in that the end of the through hole (11122) facing the brake disc assembly (12) opens into the groove bottom of the groove (11121).

9. The disc brake (1) according to claim 7, characterized in that the groove (11121) is configured as a linear groove, the parallel sides of which, viewed in the cross-sectional plane of the bearing flange (112), are tangent to the through-opening (11122).

10. The disc brake (1) according to claim 4, characterized in that the first groove (1111) and the second channel (1112) are arranged in pairs with each other and the first groove (1111) and the second channel (1112) are evenly distributed around the axis of the spindle (11).