CN116241581A

CN116241581A - Hydrodynamic retarder and vehicle

Info

Publication number: CN116241581A
Application number: CN202310014145.6A
Authority: CN
Inventors: 郭林; 胡楚金; 朱琦; 王晨凯; 宋凯
Original assignee: Zhejiang Wanliyang Transmission Co Ltd
Current assignee: Zhejiang Wanliyang Transmission Co Ltd
Priority date: 2023-01-05
Filing date: 2023-01-05
Publication date: 2023-06-09

Abstract

The invention relates to the technical field of automobiles, and discloses a hydraulic retarder, which comprises a retarder shell, wherein a retarder cover is arranged outside the retarder shell; the working cavity is positioned in the retarder and is connected with the retarder cover; the stator is fixed on the retarder cover through bolts and positioned in the working cavity, and a bearing seat is arranged on the stator; the rotor is connected with the retarder cover and is positioned in the working cavity; the input shaft is arranged at one side of the working cavity and is connected with the rotor; the flange shaft axially penetrates through the retarder shell; the bearing comprises a bearing, wherein an outer ring of the bearing is connected with a bearing seat, an inner ring of the bearing is arranged on a shaft diameter ring, and the shaft diameter ring is axially positioned through a flange shaft; and one end of the separating spring is connected with the rotor, and the other end of the separating spring is connected with the spring retainer ring. The hydraulic retarder disclosed by the invention can increase the distance between the stator and the rotor blades when the retarder is in a non-working state, and can improve and reduce the power loss of a vehicle in a running state.

Description

Hydrodynamic retarder and vehicle

Technical Field

The invention relates to the technical field of automobiles, in particular to a hydrodynamic retarder and a vehicle.

Background

The hydrodynamic retarder is a device for generating retarding action by utilizing liquid damping. The stator of the hydrodynamic retarder is connected with the rear end of the speed changer or the frame, the rotor is connected with the transmission shaft through the hollow shaft, and the rotor and the stator are cast with blades. During operation, pressure is applied to the oil pool by means of operation of the control valve, so that working fluid is filled into the working cavity between the rotor and the stator, a torque acts on the stator through the working fluid when the rotor rotates, and the counter torque of the stator becomes the braking torque of the rotor. The kinetic energy of the automobile is consumed by friction of working fluid and impact on a stator to be converted into heat energy, so that the temperature of the working fluid is increased, the working fluid is introduced into a heat exchanger to circularly flow, heat is transferred to cooling water, and the cooling water is dissipated through an engine cooling system. The hydrodynamic retarder takes over 80% to 90% of the service braking with its strong braking torque. The driving safety is ensured, and the abrasion of the brake is greatly reduced. The operation is simple, the braking is soft, the response is sensitive, the braking moment is large, the weight is light, and the speed control on a long slope is constant.

In the prior art, when the hydraulic retarder of the main stream in the market is in a non-working state, the distance between the stator and the rotor is too short, the rotor agitates air and acts on the stator under the influence of air flow, so that no-load braking torque is generated, unnecessary fuel loss is caused, and the requirements of the whole vehicle in the aspect of economy are not met.

Disclosure of Invention

The invention aims at solving the problem that a certain power loss is caused by air flow when the hydraulic retarder is in a non-working state in the prior art, and aims to reduce the no-load power loss of the retarder in the non-working state on the premise of ensuring the normal working of the retarder so as to improve the fuel economy of a vehicle.

The technical scheme adopted by the device is as follows: the hydraulic retarder comprises a retarder shell, wherein a retarder cover is arranged outside the retarder shell;

the working cavity is positioned in the retarder and is connected with the retarder cover;

the stator is fixed on the retarder cover through bolts and positioned in the working cavity, and a bearing seat is arranged on the stator;

the rotor is connected with the retarder cover and is positioned in the working cavity;

the input shaft is arranged at one side of the working cavity and is connected with the rotor;

the flange shaft axially penetrates through the retarder shell;

the bearing comprises a bearing, wherein an outer ring of the bearing is connected with a bearing seat, an inner ring of the bearing is arranged on a shaft diameter ring, and the shaft diameter ring is axially positioned through a flange shaft;

and one end of the separating spring is connected with the rotor, and the other end of the separating spring is connected with the spring retainer ring.

Preferably, the rotor is connected with the input shaft through a shaft spline, and the rotor is provided with a bevel spline.

Preferably, the oblique spline comprises a rotor internal spline and a rotor external spline, and the rotor internal spline and the rotor external spline are in small clearance fit.

Preferably, the left side of the rotor is connected with a positioning shaft shoulder, and the right side of the rotor is connected with a separating spring.

Preferably, the positioning shaft shoulder is in a shaft-shaped structure in a step-shaped arrangement, and the side surface of the positioning shaft shoulder plays a role in positioning the rotor.

Preferably, the spring retainer ring on the separating spring is a metal pad with an inner ring and an outer ring, and the outer ring part is of a stepped circular structure.

Preferably, the outer ring of the spring retainer ring is further fixed with the bearing in a clearance fit manner, and the spring retainer ring and the bearing are fixed and then are mounted on the shaft diameter ring together.

Preferably, a pump upper cover is arranged in the retarder, and a pump upper cover oil inlet hole is formed in the pump upper cover; a pump lower shell is arranged below the pump upper cover, and a pump lower shell oil outlet hole is arranged on the pump lower shell.

Preferably, an oil storage chamber is arranged at the bottom of the retarder and is used for receiving oil flowing back from the working cavity.

The present application also provides a vehicle comprising a hydrodynamic retarder as described above.

The hydraulic retarder provided by the invention has the following specific working processes: when the retarder is in a working state, after working fluid enters the working cavity, the retarder generates resistance, the resistance gradually increases along with gradual entry of the working fluid, the axial acting force generated on the inclined spline of the rotor increases along with the gradual entry of the working fluid, and overcomes the separation acting force of the separation spring, so that the rotor approaches to the stator, a torque acts on the stator through the working fluid when the rotor rotates, the counter torque of the stator becomes the braking torque of the rotor, and the retarder has a braking effect.

When the retarder releases the braking state, the working fluid in the working cavity flows back to the oil storage chamber, the retarder returns to the idle state, at the moment, the resistance of the retarder is greatly reduced, the axial acting force between the inclined splines of the rotor is correspondingly reduced, when the axial acting force is reduced to a value which cannot overcome the separation acting force of the separation spring, the separation spring forces the rotor to move towards a direction far away from the stator, and the separation of the stator and the rotor is realized, so that the influence on the stator is weakened when the rotor agitates air, the idle braking moment generated when the rotor agitates the air is reduced, and the power loss of the vehicle in the running state is further reduced.

Compared with the prior art, the device has the following beneficial effects: through design stator and rotor separation structure in the retarber for the retarber can be with the increase as far as possible of stator and rotor blade distance in the non-operating condition, after increasing stator and rotor blade distance, the rotor stirs the air flow and the moment that produces on the stator that acts on greatly reduced, and then reduces the power loss of vehicle under running state. The scheme is simple and reliable, has low cost, and completely meets the requirement that no-load power loss in the Q/CT1046 standard is not more than 2 KW.

Drawings

Fig. 1 is an overall cross-sectional view of an embodiment of a retarder according to the present application.

Fig. 2 is a schematic diagram of the relevant structure of the working chamber of the retarder in the present application.

Fig. 3 is a schematic view of the rotor of fig. 1.

Fig. 4 is a schematic diagram of the input shaft of fig. 1.

Fig. 5 is a schematic view of a retarder positioning shoulder in the present application.

Fig. 6 is a schematic view of a retarder spring collar in the present application.

Wherein, 1, retarder shell; 2. a retarder cover; 3. a working chamber; 4. a stator; 5. a rotor; 6. an input shaft; 7. a flange shaft; 8. a bearing; 9. a shaft diameter ring; 10. a bearing seat; 11. a separation spring; 12. a spring retainer ring; 13. a pump upper cover; 14. an oil inlet hole is formed in the upper cover of the pump; 15. a pump lower case; 16. oil outlet holes of the pump lower shell; 17. an auxiliary oil cavity; 18. an oil storage chamber; 19. positioning a shaft shoulder; 20. a beveled spline; 21. and (3) a shaft spline.

Detailed Description

In order that the above objects, features and advantages of the invention will be readily understood, a more particular description of the invention will be rendered by reference to the appended drawings. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. The present invention may be embodied in many other forms than described herein and similarly modified by those skilled in the art without departing from the spirit of the invention, whereby the invention is not limited to the specific embodiments disclosed below.

In the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.

It will be understood that when an element is referred to as being "fixed" or "disposed" on another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like are used herein for illustrative purposes only and are not meant to be the only embodiment.

As shown in fig. 1 and 2, the hydraulic retarder in the embodiment is installed at a power take-off port on an engine flywheel housing and comprises a retarder housing, and a retarder cover is arranged outside the retarder housing. The retarder shell comprises a rotor shell and a stator shell, a first half cavity for accommodating a stator is formed in one side of the stator shell, and a second half cavity for accommodating a rotor is formed in one side of the rotor shell.

The working cavity is positioned in the retarder and is connected with the retarder cover. The working chamber is divided into a first half chamber for accommodating the stator and a second half chamber for accommodating the rotor, when the hydraulic retarder is in a working state (i.e. when the braking effect is achieved), working fluid starts to flow from the oil storage chamber towards the upper pump cover, flows into the upper pump cover through the oil inlet hole of the upper pump cover, further enters the working chamber, and continuously flows in the working chamber.

The stator is fixed on the retarder cover through bolts and positioned in the working cavity, and the stator is provided with a bearing seat. The stator is positioned in a first half cavity in the working cavity and is fixedly arranged on the shell of the retarder through bolts. The bearing pedestal is used for positioning the mounting position of the bearing and supporting the bearing.

As shown in fig. 3 and 5, the rotor is connected to the retarder cover and located inside the working chamber. The rotor spline comprises a rotor internal spline and a rotor external spline, and the internal spline and the external spline of the rotor are in small clearance fit. The left side of the rotor is positioned by a positioning shaft shoulder, the positioning shaft shoulder is connected with a spline shaft of the rotor, the spline shaft is manufactured into a shaft shoulder structure in a stepped shaft processing mode, and the mounting position of the rotor is determined through the side surface of the shaft shoulder.

As shown in fig. 4, an input shaft is provided at one side of the working chamber and connected to the rotor. The rotor is connected with the input shaft through a shaft spline, and the input shaft is connected with a transmission shaft of the engine power take-off port through an end flange, so that the rotor rotates along with the input shaft.

And the flange shaft axially penetrates through the retarder shell. The flange shaft is used as a supporting structure, and can play an auxiliary positioning role in the installation of the journal ring, the pump upper cover and the pump lower shell.

The bearing is characterized in that an outer ring of the bearing is connected with the bearing seat, an inner ring of the bearing is arranged on the shaft diameter ring, and the shaft diameter ring is axially positioned through the flange shaft. The bearing outer ring is positioned by the bearing seat, and the bearing inner ring is arranged on the shaft diameter ring and positioned by the shaft diameter ring.

And one end of the separating spring is connected with the rotor, and the other end of the separating spring is connected with the spring retainer ring. As shown in fig. 6, the right end of the spring retainer ring is positioned by means of a bearing, and the inner side edge of the spring retainer ring has a certain inclination angle, so that the spring retainer ring is convenient to install on the shaft diameter ring.

Specifically, the rotor is connected with the input shaft through a shaft spline, and the rotor is provided with an inclined spline. The internal and external splines of the rotor can be called as the bevel splines because the helical angles of the internal and external splines of the rotor are larger, and the external and external splines of the rotor have spline appearances with larger inclination angles.

Specifically, the positioning shaft shoulder is in a shaft-shaped structure in a step-shaped arrangement, and the side surface of the positioning shaft shoulder plays a role in positioning the rotor. The positioning shaft shoulder is of a structure on the input shaft, and shafts which are arranged in a step shape on the shaft shoulder are matched with the spline of the rotor to play a role in positioning the rotor.

Specifically, a pump upper cover is arranged in the retarder, and a pump upper cover oil inlet hole is formed in the pump upper cover; a pump lower shell is arranged below the pump upper cover, and a pump lower shell oil outlet hole is arranged on the pump lower shell. When the retarder works, working fluid enters the pump upper cover from the oil storage chamber through the pump upper cover oil inlet hole and further flows into the working cavity, at the moment, the rotor drives the working fluid to rotate together under the driving of the input shaft, and the viscous effect of the working fluid enables the rotor to receive viscous resistance of the stator, so that braking torque is generated, and the rotating speed of the rotor is reduced. When the retarder stops working, working fluid flows back from the working cavity, flows into the pump lower shell through the pump lower shell oil outlet hole and flows back to the oil storage chamber, viscous resistance is not applied to the working fluid in the working cavity at the moment, and the vehicle keeps normal running.

Specifically, based on the same inventive concept, the embodiment of the application also provides a vehicle, which comprises the hydraulic retarder in the embodiment.

The specific working process of the retarder in this embodiment is as follows:

(1) When the hydraulic retarder is in a working state, namely when a vehicle needs to be braked and decelerated, working fluid enters the pump upper cover from the oil storage chamber through the pump upper cover oil inlet hole and further flows into the working cavity, at the moment, the rotor drives the working fluid to rotate together under the drive of the input shaft, the viscous action of the working fluid enables the rotor to receive the viscous resistance of the stator, along with the gradual entering of the working fluid, the resistance is continuously increased, further axial acting force on the rotor inclined spline is also continuously increased, the axial acting force is opposite to the separating acting force direction of the separating spring, the acting force of the separating spring can be finally overcome, the rotor is enabled to approach the stator, the stator applies larger reaction force to the rotor, further continuously increased braking torque is generated, the rotating speed of the rotor is continuously reduced, and the effect of reducing the vehicle speed is achieved.

(2) When the hydraulic retarder is in a non-working state, namely when the vehicle does not need to brake and decelerate, working fluid flows back from the working cavity, flows into the pump lower shell through the oil outlet of the pump lower shell and flows back into the oil storage chamber, the working cavity is free of working fluid, the retarder returns to an idling state, the resistance to which the rotor is subjected is greatly reduced, the axial acting force between inclined splines of the rotor is correspondingly reduced, the separating acting force of the separating spring cannot be overcome finally, the separating spring forces the rotor to move in a direction far away from the stator due to rebound effect, separation of the stator and the rotor is realized, at the moment, the influence of air stirring by the rotor on the stator is weak, the idling braking moment of the retarder is reduced, and the power loss of the retarder under the running state of the vehicle is further reduced.

The retarder of the embodiment has the advantages that the separation spring is reasonably arranged, so that when the retarder is in a non-working state, the distance between the blades of the stator and the rotor is increased as much as possible, and no-load braking moment generated by the rotor due to air disturbance is reduced. In the scheme, the separation distance of the stator and the rotor blades reaches 17.25 mm, and the actual test shows that the requirement that the no-load power loss in the Q/CT1046 standard is not more than 2KW is completely met.

The hydraulic retarder provided in the embodiment of the application is used for auxiliary braking of a vehicle, and of course, can also be used in other working conditions suitable for the hydraulic retarder, and is not limited herein.

The above examples illustrate only a few embodiments of the invention, which are described in detail and are not to be construed as limiting the scope of the invention. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the invention, which are all within the scope of the invention. Accordingly, the scope of protection of the present invention is to be determined by the appended claims.

Claims

1. The hydraulic retarder is characterized by comprising a retarder shell, wherein a retarder cover is arranged outside the retarder shell;

the flange shaft axially penetrates through the retarder shell;

2. The hydrodynamic retarder according to claim 1, wherein the rotor is connected with the input shaft by a shaft spline, and the rotor is provided with a bevel spline.

3. The hydrodynamic retarder of claim 2, the diagonal spline comprising a rotor internal spline and a rotor external spline, the rotor internal spline and the rotor external spline employing a small clearance fit.

4. The hydrodynamic retarder of claim 2, wherein the rotor has a left side connected to a locating shoulder and a right side connected to a separating spring.

5. The hydraulic retarder of claim 4, wherein the positioning shoulders are shaft-shaped structures arranged in a step-like manner, and the sides of the positioning shoulders play a role in positioning the rotor.

6. The hydraulic retarder of claim 1, wherein the spring retainer ring on the separating spring is a metal pad with an inner ring and an outer ring, and the outer ring is in a stepped circular structure.

7. The hydrodynamic retarder of claim 6, wherein the outer ring of the spring collar is fixed to the bearing by a clearance fit, and the spring collar is mounted to the shaft collar after the spring collar is fixed to the bearing.

8. The hydraulic retarder according to claim 1, wherein a pump upper cover is arranged in the retarder, and a pump upper cover oil inlet hole is arranged on the pump upper cover; a pump lower shell is arranged below the pump upper cover, and a pump lower shell oil outlet hole is arranged on the pump lower shell.

9. A hydraulic retarder according to claim 1, wherein an oil reservoir is provided at the bottom of the retarder for receiving oil flowing back from the working chamber.

10. A vehicle comprising a hydrodynamic retarder according to any of claims 1-9.