JPH0556713U - Brake booster - Google Patents

Abstract

(57) [Summary] (Correction) [Purpose] A large braking effect is obtained with a small braking pressure by indirectly performing the braking operation of the drive shaft. [Structure] The input gears 2 and 3 are fixedly provided on the drive shaft 1. A differential gear device 7 provided in parallel with the shaft 1 is composed of sun gears 8 and 9, planetary gears 10 and 11, a gearbox 12, and a ring gear 13 fixed to the gearbox. The planetary gears 10 and 11 are meshed with each other at the same time. The sun gears 8 and 9 are configured to mesh with each other. Gear 4,
5 is on the same axis as the differential gear unit 7, the gear 4 is connected to the sun gear 8, and the gear 5 is connected to the sun gear 9. The input gear 2 meshes with the gear 4, the input gear 3 meshes with the intermediate gear 6, and the intermediate gear 6 meshes with the gear 5. The gear 13 meshes with the gear 14, and the gear 14 is connected to the brake disc 15. The rotation of the drive shaft 1 and the rotation of the brake disc 15 are proportional to each other, and the braking action of the drive disc 1 can be performed by the braking action of the brake disc 15.

Description

Description [0001] [0001] [Industrial field of application] The present invention relates to a brake booster capable of obtaining a large braking force with a small force. [0002] [Prior Art] There are many types of braking devices for automobiles, railway vehicles, etc., but most of the mechanisms that generate braking force are the pressure applied to the rotating body except some auxiliary braking devices. It is due to friction caused by, and performs a braking action by converting kinetic energy into heat energy. Therefore, technological progress corresponding to the increase in load caused by higher speed and larger size has mainly been directed to strengthening brake pressure and improving the performance of friction devices. There are hydraulic devices, hydraulic boosters, air brake devices, etc. for strengthening the brake pressure, and drum brakes, disk brakes, etc. for improving the performance of the friction device. However, since such equipment is large and requires high technology, the cost is also high and runs counter to the need to reduce the weight of the vehicle. In addition, the increase in load caused by high speed and weight does not solve the problem simply by increasing the size of the equipment, but countermeasure technology such as friction material wear countermeasures such as lining, friction heat radiation countermeasures, etc. Needed. [0003] [Problems to be solved by the invention] The present invention aims to reduce the rotational energy of the drive shaft due to the interposition of a differential device and obtain a high braking effect with a small brake pressure. [0004] [Means for Solving the Problems] (a) The rotation of the drive shaft 1 is divided into two paths via a gear 2 and a gear 3 that are coaxially fixed and is a gear that is an input element of the differential gear device 7. 8 and the gear 9. (B) The gear ratio between the constituent gears is set so that the amount of rotation transmitted through the gears 2 to 8 path and the amount of rotation transmitted through the gears 3 to 9 paths are different. (C) The differential gear device 7 is arranged so that the rotations transmitted through the gears 2 to 8 paths and the rotations transmitted through the gears 3 to 9 cancel each other out, and the difference in rotation is the rotation of the gear 13 of the output element. (D) A braking device is provided on the gear 13, which is an output element of the differential gear device. With the above configuration, the braking action of the drive shaft 1 is indirectly performed by the braking action of the output element on the gear 13. [Operation] The rotation of the drive shaft 1 rotates the gears 2 and 3, and the gear 2 drives the gear 8 via the gear 4. The gear 3 drives the gear 9 via the intermediate gear 6 and the gear 5. Since the reduction ratios of the gears 2 to 8 and the gears 3 to 9 are different, the rotation speeds of the gears 8 and 9 are different. Further, the rotation of the gears 8 and 9 which are the input elements of the differential gear device are offset by the action of the intermediate gear 6, and the difference in rotation is the rotation of the gear 13 of the output element. Therefore, the rotational speeds of the drive shaft 1 and the output element gear 13 are in direct proportion, but the rotational speed or torque amount transmitted to the gear 13 is greatly reduced. Therefore, the braking operation of the brake disc 15 which is interlocked with the gear 13 via the gear 14 can be performed with an extremely small braking pressure. When the rotation of the gear 13 is stopped by the braking action on the brake disk 15, the rotation transmitted in the gears 2 to 8 path and the rotation number transmitted in the gears 3 to 9 path are different, and the non-rotation phenomenon occurs in the entire device. Then, the rotation of the drive shaft 1 also stops. Further, since the rotation speed of the gear 13 and the rotational speed of the drive shaft 1 are always in direct proportion, when the gear 13 is decelerated by the braking action applied to the disc brake 15, the drive shaft 1 is decelerated in proportion to the gear 13. Therefore, it is also possible to perform a braking action such as a deceleration operation or a gradual stop. When the braking action on the brake disk 15 is released and the braking pressure is not applied to the rotation of the gear 13, the gear 13 rotates in proportion to the rotation of the drive shaft, so that the braking action does not work on the drive shaft 1 and the rotation of the drive shaft 1 The brake booster does not limit the rotation. [0006] [Example 1] Fig. 1 shows Example 1. The differential device 7 used in this embodiment is fixed to the sun gears 8 and 9, planetary gears 10 and 11, which act as input elements, the gearbox 12 which acts as a carrier, and the gearbox 12, which acts as an output element. The ring gear 13 is formed so that the planetary gears 10 and 11 mesh with each other and at the same time the planetary gear 10 meshes with the sun gear 8 and the planetary gear 11 meshes with the sun gear 9. The input gears 2 and 3 are fixedly provided on the drive shaft 1. The differential device 7 is on an axis provided parallel to the drive shaft 1 and the sun gear 8 is connected to the gear 4 and the sun gear 9 is connected to the gear 5. The gear 4 meshes with the gear 2 and the gear 5 is connected to the gear 3 via an intermediate gear 6. The ring gear 13 of the differential gear device meshes with a gear 14, and the gear 14 is connected to a brake disk 15. The rotation of the drive shaft 1 is transmitted to the gear 8 through the gears 2 and 4 and to the gear 9 through the gears 3, 5 and 6, but the intermediate gear 5 causes the gears 8 and 9 to rotate in opposite directions to cancel each other. Each other. The gearbox 12 and the ring gear 13 rotate due to the rotation difference between the gears 8 and 9, and the rotation of the ring gear 13 drives the brake disk 15 via the gear 14. If the number of gears of the sun gears 8 and 9 and the number of gears of the planetary gears 10 and 11 of the differential gear device are equal, the gear ratio between the gears 2 and 4 is set to 1: 1 and the gear ratio between the gears 3 and 5 is set to 1: 1. Is set to 6: 5 and the gear ratio between the ring gear 13 and the gear 14 is set to 5: 1, the shaft 1 Decrease. Therefore, the amount of friction required for the braking action of the brake disc 15 is applied to the drive shaft. [0007] [Second Embodiment] FIG. 2 shows a second embodiment. The differential gear device 7 used in this embodiment supports a pair of sun gears 8 and 9 and a pair of planetary gears 10 and 11 which mesh with the sun gears 8 and 9 and are fixed on the same shaft. A gear box 12 that plays the role of a carrier and a ring gear 13 that interlocks with the gear box 12 are included. The input gears 2 and 3 are fixedly provided on the drive shaft 1. The differential gear device 7 is on an axis provided parallel to the drive shaft 1, the sun gear 8 is connected to the gear 4, and the sun gear 9 is connected to the gear 5. The gear 2 meshes with the gear 4 and the gear 3 meshes with the gear 5. The rotation of the drive shaft 1 is transmitted to the sun gears 8 and 9, but the rotations of both gears cancel each other out, and the difference in rotation causes the ring gear 13 to rotate. The rotation of the ring gear 13 drives the brake disk 15 via the gear 14. [0008] [Third Embodiment] FIG. 3 shows a third embodiment. The differential gear device 7 used in the present embodiment is a bevel gear type differential gear device, and a pair of bevel gear side gears 16 and 17, bevel gear differential pinions 18 and 19 and a differential pinion that mesh at right angles with the side gears are supported to support a shaft. It is composed of a ring gear 20 provided integrally with a carrier that rotates in the center. In this embodiment, one side gear and the ring gear of the differential gear device are input elements, and the other side gear is an output element. The input gears 2, 3 are fixedly provided on the drive shaft 1. The differential gear device 7 is on an axis provided parallel to the drive shaft 1, the side gear 16 is connected to the gear 4, and the side gear 17 is connected to the gear 21. The gear 2 meshes with the gear 4 and the gear 3 meshes with the ring gear 20. The gear 21 meshes with the gear 14, and the gear 14 is connected to the brake disc. The rotation of the drive shaft 1 is transmitted to the side gear 16 and the ring gear 20, but the rotations of both gears cancel each other out, and the difference in rotation drives the side gear 17, and drives the brake disc 15 via the gear 21 and the gear 14. [Effect] When an indirect braking mechanism is configured through a brake booster, it is possible to perform a braking operation with an extremely small braking force as compared with a case where a braking device is directly provided on the drive shaft, and thus a lower position. It is possible to obtain a high-level braking effect with various braking devices.

BRIEF DESCRIPTION OF THE DRAWINGS [FIG. 1] A perspective view of a first embodiment. FIG. 2 is a perspective view of a second embodiment. FIG. 3 is a perspective view of a third embodiment. [Explanation of reference symbols] 1 Drive shafts 2, 3
Input gears 4, 5 Transmission gears 6
Intermediate gear 7 Differential gear device 8, 9
Sun gears 10, 11 Planetary gears 12
Gear box 13 ring gear 14
Transmission gear 15 Brake disk 16, 17
Side gears 18, 19 Differential pinion 20
Ring gear 21 Transmission gear

Claims (1)

[Claims for utility model registration] [Claim 1] b) The rotation of the drive shaft (1) is divided into two paths via a gear (2) and a gear (3) that are coaxially fixed, and a differential gear device ( It is configured to be transmitted to the gear (8) and the gear (9) which are the input elements of 7). (B) The gear ratio between the constituent gears is set so that the rotation amount transmitted through the gears (2) to (8) route and the rotation amount transmitted through the gears (3) to (9) route are different. C) Rotation transmitted through the gears (2) to (8) and the gear (3)
(9) The differential gear device (7) is arranged so that the rotations transmitted through the paths cancel each other out, and the rotation difference causes the rotation of the gear (13) of the output element. D) Gear (13) which is an output element of the differential gear device (7)
Install a braking device on. A brake booster configured as described above for braking the drive shaft (1) by braking the gear (13).