CN212643384U - Rotor separable hydraulic retarder - Google Patents

Abstract

The utility model discloses a hydraulic retarder with a separable rotor; the retarder shaft is connected with the power driving structure in a torsion-resistant manner through a spline; the right end of the separating spring seat is arranged on a shaft shoulder of the retarder shaft, and the left side of the separating spring seat acts on the meshing gear; the synchronizing ring is arranged behind the meshing gear, the outer friction conical surface of the synchronizing ring is matched with the inner friction conical surface of the rotor, and synchronous torque is generated during meshing; the retarder shaft rotates when the vehicle runs normally and is unloaded; the integral separable rotor is skillfully arranged in front of the stator and the rotor, and the active meshing gear and the rotor are organically combined to form a whole, so that the operation is stable, the space interest rate is high, the structure is compact, the stress of the meshing gear is reasonably and effectively reduced, and the weight of components is effectively controlled. The annular meshing air cylinder or oil cylinder and the separating spring are coaxially arranged in parallel, so that the space is effectively utilized, and the interference is avoided. The rotor meshing teeth are arranged above the arc of the blade, so that the stress of the gear and the meshing separation force are reduced, the rigidity of the separation spring can be reduced, the space size is reduced, and the arrangement is convenient.

Description

Rotor separable hydraulic retarder

Technical Field

The utility model belongs to the technical field of automobile engineering, a rotor detachable hydraulic retarber is related to.

Background

A hydrodynamic retarder is a retarder for reducing the running speed of a vehicle by a hydrodynamic device, and is also called a hydrodynamic retarder.

At home and abroad, the regulations require that heavy trucks or buses are matched with hydraulic retarders, but the idling loss is required to be as small as possible when the heavy trucks or buses do not require deceleration, namely idling. Most of the conventional hydraulic retarders have large idle load loss, and how to reduce the idle load loss of the hydraulic retarders is a technical subject.

Disclosure of Invention

The utility model discloses a rotor detachable hydraulic retarber to solve the great scheduling problem of hydraulic retarber idle loss among the prior art.

The utility model comprises a retarder shaft, an end face bearing, an end cover, a power driving structure, a rotor, a stator, a body, a rear end cover, a bearing bracket, a rear bearing, a working cavity oil seal, a front oil seal and a gear shifting separation structure; the power input end of the product is taken as the front; the front bearing is arranged and installed behind the power input gear and is embedded at the left side of the end cover; the rear bearing outer sleeve is embedded on the bearing support; the rotor is axially positioned with the stator through the end face bearing, the stator inner hole and the positioning snap ring; the stator, the end cover and the body form circumferential and axial positioning; the power driving structure and the annular end face bearing are arranged in an annular cylinder body of the end cover, and the power driving structure is an annular piston; the retarder shaft is connected with the power driving structure in a torsion-resistant manner through a spline; the gear shifting separation structure comprises an engaging gear, a separation spring and a synchronous ring; the right end of the separating spring seat is arranged on a shaft shoulder of the retarder shaft, and the left side of the separating spring seat acts on the meshing gear; the synchronizing ring is arranged behind the meshing gear, the outer friction conical surface of the synchronizing ring is matched with the inner friction conical surface of the rotor, and synchronous torque is generated during meshing; the meshing gear overcomes the separation spring to realize meshing with the rotor under the pushing of the power driving structure, and the rotor, the meshing gear and the retarder shaft form an integral co-rotation; the retarder shaft rotates when the vehicle runs normally and is unloaded; when the brake is released, the driving force of the power driving structure is removed, the meshed gear is separated from the rotor under the action of the separation spring and returns to the left positioning position, the rotor does not rotate with the retarder shaft, no braking force is generated, and the brake is in no-load operation; when the rotor is in idle load, the power driving structure does not compress air, and the separation spring pushes the meshing gear to the left positioning position and simultaneously separates the meshing gear from the meshing teeth of the rotor.

The utility model discloses an optimized scheme, the gear shift separation structure also includes synchronous lock ring, bearing, elastic snap ring, spline hub, spring ring, slider; the annular piston is always contacted with the meshing gear through the end face bearing, so that the annular piston does not rotate along with the meshing gear; the slide block is arranged in the groove of the spline hub; the sliding block is matched with the groove on the spline hub and can slide left and right; meanwhile, the sliding block is matched with the groove of the synchronous ring; the outer circle of the sliding block is provided with an annular bulge which is matched with an annular groove of an internal spline of the meshing gear, so that the left and right positioning effect is realized, and the sliding block can slide relative to the spline hub; the meshing gear is connected with a retarder shaft to transmit braking torque; the rotor shaft sleeve is supported on the excircle of the meshing gear shaft sleeve through a bearing, so that the meshing gear can conveniently slide left and right on the retarder shaft; the spring ring is pressed on the inner teeth of the meshing gear; the spline hub is matched with the bearing to rotate; the inner hole of the spline hub is matched with a small shaft shoulder protruding from the rotor, one end of the elastic clamping ring is embedded on the rotor, and the other end of the elastic clamping ring compresses the spline hub to enable the spline hub to be static relative to the axial direction of the rotor.

The utility model relates to an optimized scheme, meshing gear passes through the spline for the butterfly and is connected with the retarber hub connection.

The utility model discloses a scheme of optimizing, shift separation structure slider quantity more than or equal to two has the circumference equipartition groove that equals with slider quantity on the spline hub, and the slider is arranged at spline hub equipartition inslot, and the slider cooperates with the equipartition groove of synchronizer ring simultaneously.

According to an optimized scheme, three sliding blocks are arranged in three uniformly distributed grooves of the spline hub.

The groove width of the synchronizing ring is wider than that of the sliding block, when the friction conical surface of the synchronizing ring is just in contact with the friction conical surface of the rotor, the reverse limiting position of the synchronizing ring just enables the tooth conical surface of the end face at the right side of the meshing gear to be abutted against the tooth conical surface at the left end of the synchronizing ring for locking, and after synchronization, the synchronous meshing can be realized by clockwise rotating half teeth through the torque of the driving plate; when the meshing is asynchronous before the meshing, a reverse moment is generated when the conical surface of the right tooth end of the meshing gear is just contacted with the conical surface of the left tooth end of the synchronizing ring, so that the spline teeth of the synchronizing ring are better opposite to the conical surface of the meshing gear, and meshing and tooth beating are prevented when the meshing gear and the rotor are asynchronous; when in synchronization, the friction torque disappears, and the torque of the drive plate drives the rotor and the synchronous ring to move forward by half of the teeth to be smoothly meshed.

When meshing, the sliding block and the spline are matched and enter the meshing gear; the slide block is matched with the synchronizing ring through a groove, and the synchronizing ring and the meshing gear rotate simultaneously.

When braking, the power driving structure pushes the meshing gear backwards, the meshing gear drives the synchronous ring to be close to the rotor, and the sliding block can slide relative to the spline hub without leaving a positioning position; when the synchronous ring friction conical surface is contacted with the rotor friction conical surface, a reverse torque is formed, so that the right end tooth conical surface of the meshing gear is opposite to the end tooth conical surface of the synchronous ring to be locked, and the synchronous ring is pressed towards the rotor; when the friction torque of the friction conical surface is gradually increased to the point that the rotor and the meshing gear are synchronous, the friction torque gradually disappears, and the clockwise drive plate torque can drive the synchronous ring forwards to be smoothly meshed; after meshing, corresponding media are supplied to the working cavity to generate corresponding braking force.

When the gear is unloaded, the spline hub and the meshing gear rotate simultaneously; the outer circle of the sliding block is provided with a bulge which is matched and positioned with a circular groove at the position of an internal spline of the meshing gear, and the synchronizing ring is arranged outside the left side end surface of the meshing gear; the rotor does not rotate with the retarder shaft, the meshing gear rotates with the retarder shaft, and the meshing gear is disengaged from the meshing teeth of the rotor under the action of the separation spring and returns to the limiting position at the front end; the working cavity of the stator and the rotor only has a small amount of medium.

The sealing ring separates the working cavity from the liquid supplementing cavity behind the rotor; sealing the excircle of the stator by an O-shaped seal; a front oil seal behind the bearing prevents lubricating oil of the gearbox from entering the retarder; the working cavity oil seal seals working media in the working cavity, the pressure reducing ring prevents high-pressure media from influencing the sealing performance of the oil seal, and the lubricating of a sealing lip of the oil seal is lubricated by a special oil pump through a shaft center oil delivery hole; in the end cover, the end cover and the body are provided with rotors and stators to form a working cavity, and when working media such as oil or cooling liquid are filled in the working cavity, the rotors can generate certain resistance to generate braking force when rotating.

The utility model has the advantages of: the hydraulic retarder has the advantages of few integral parts, compact structure, small volume, convenient installation, reduction of no-load loss and improvement of the performance of the hydraulic retarder; the integral separable rotor is skillfully arranged in front of the stator and the rotor, and the active meshing gear and the rotor are organically combined to form a whole, so that the operation is stable, the space interest rate is high, the structure is compact, the stress of the meshing gear is reasonably and effectively reduced, and the weight of components is effectively controlled. The annular meshing air cylinder or oil cylinder and the separating spring are coaxially arranged in parallel, so that the space is effectively utilized, and the interference is avoided. The rotor meshing teeth are arranged above the arc of the blade, so that the stress of the gear and the meshing separation force are reduced, the rigidity of the separation spring can be reduced, the space size is reduced, and the arrangement is convenient. Meanwhile, compressed air of the cylinder or hydraulic oil of the hydraulic oil cylinder can be skillfully led into the back of the annular piston and can be controlled through the switch valve, and the device is simple and reliable. The cost is low.

Drawings

FIG. 1 is a schematic structural view of the present invention;

FIG. 2 is a partially enlarged schematic view of the present invention;

in the figure: 1 retarder axle, 2 front bearings, 3 end covers, 4 power drive structures, 5 synchronous lock rings, 6 meshing gears, 7 rotors, 8 stators, 9 bodies, 10 rear end covers, 11 bearing supports, 12 rear bearings, 13 separation springs, 14 working cavity oil seals, 15 front oil seals, 16 bearings, 17 elastic snap rings, 18 spline hubs, 19 spring rings, 20 sliders and 21 synchronous rings.

Detailed Description

The following describes embodiments of the present invention in detail with reference to the drawings.

The first embodiment of the present invention is shown in fig. 1 and fig. 2, and includes a retarder shaft 1, an end face bearing 2, an end cover 3, a power driving structure 4, a rotor 7, a stator 8, a body 9, a rear end cover 10, a bearing bracket 11, a rear bearing 12, a working chamber oil seal 14, a front oil seal 15, and a gear shifting separation structure; the power driving structure 4 is an oil cylinder; the power input end of the product is taken as the front; the front bearing 2 is arranged and installed behind the power input gear and is embedded at the left side of the end cover 3; the rear bearing 12 is sleeved and embedded on the bearing support 11; the rotor 7 is axially positioned with the stator through the end face bearing 2, the inner hole of the stator 8 and the positioning snap ring, and the working cavity is separated from the liquid supplementing cavity behind the rotor through the sealing ring. The stator 8, the end cover 3 and the body 9 form circumferential and axial positioning, and the excircle of the stator is sealed by an O-shaped seal; a front oil seal 15 behind the bearing prevents the lubricating oil of the gearbox from entering the retarder; the working cavity oil seal 14 seals working cavity working media, the pressure reducing ring prevents high-pressure media from influencing the sealing performance of the oil seal, and the lubricating of a sealing lip of the oil seal is lubricated by a special oil pump through a shaft center oil delivery hole; the power driving structure 4 and the annular end face bearing are arranged in an annular cylinder body of the end cover 3, and the power driving structure 4 is an annular piston; the retarder shaft 1 is connected with the power driving structure 4 in an anti-torsion mode through a spline, and the retarder shaft 1 rotates when the vehicle runs normally and is unloaded; in the end cover 3, the end cover 3 and the body 9 are provided with the rotor 7 and the stator 8 to form a working cavity, and when working media such as oil or cooling liquid are filled in the working cavity, the rotor 7 can generate certain resistance to generate braking force when rotating.

The gear shifting separation structure comprises a synchronous locking ring 5, a meshing gear 6, a separation spring 13, a bearing 16, an elastic snap ring 17, a spline hub 18, a spring ring 19, a sliding block 20 and a synchronous ring 21; the annular piston is always contacted with the meshing gear 6 through the end face bearing 2, so that the annular piston does not rotate along with the meshing gear 6; the three slide blocks 20 are arranged in three evenly distributed grooves of the spline hub 18; the sliding block 20 is matched with a groove on the spline hub 18 and can slide left and right; meanwhile, the sliding blocks are matched with the uniformly distributed grooves of the synchronizing ring 21; the outer circle of the sliding block 20 is provided with an annular bulge which is matched with an annular groove of an internal spline of the meshing gear, plays a role in left and right positioning and can slide relative to the spline hub 18; the meshing gear 6 is in a butterfly shape and is connected with the retarder shaft 1 through a spline to transmit braking torque; the rotor shaft sleeve is supported on the outer circle of the shaft sleeve of the meshing gear 6 through a bearing, so that the meshing gear 6 can conveniently slide left and right on the retarder shaft 1; the spring ring 19 presses on the internal teeth of the meshing gear 6; the spline hub 18 is matched with the bearing 16 for rotation; an inner hole of the spline hub 18 is matched with a small shaft shoulder protruded from the rotor, one end of an elastic snap ring 17 is embedded on the rotor 7, and the other end of the elastic snap ring compresses the spline hub to enable the spline hub to be static relative to the axial direction of the rotor; the right end of the separating spring seat 13 is arranged on a shaft shoulder of the retarder shaft 1, and the left side of the separating spring seat acts on the meshing gear 6; the synchronizing ring 21 is arranged behind the meshing gear 6, the outer friction conical surface of the synchronizing ring 21 is matched with the inner friction conical surface of the rotor 7, and synchronous torque is generated during meshing; the meshing gear 6 overcomes the separation spring 13 to realize meshing with the rotor under the pushing of the power driving structure 4, and the rotor 7, the meshing gear 6 and the retarder shaft 1 form an integral co-rotation; when the brake is released, the driving force of the power driving structure 4 is removed, the meshed gear 6 is separated from the rotor 7 under the action of the separation spring 13 and returns to the left side positioning position, the rotor 7 does not rotate with the retarder shaft 1, no braking force is generated, and no-load operation is realized; when the power driving structure 4 is not supplied with compressed air during idling, the separation spring 13 pushes the meshing gear 6 to the left positioning position, and simultaneously the meshing gear 6 is separated from the meshing teeth of the rotor 7.

The groove width of the synchronizing ring 21 is larger than the width of the sliding block, when the friction conical surface of the synchronizing ring 21 is just contacted with the friction conical surface of the rotor 7, the reverse limiting position of the synchronizing ring 21 just enables the right end surface tooth conical surface of the meshing gear 6 to be propped against the left end tooth conical surface of the synchronizing ring 21 to be locked, and after synchronization, half tooth can be clockwise rotated through the torque of the driving plate to realize synchronous meshing; when the meshing is asynchronous, a reverse moment is generated when the conical surface of the right tooth end of the meshing gear 6 is just contacted with the conical surface of the left tooth end of the synchronizing ring 21, so that the spline teeth of the synchronizing ring are better opposite to the conical surface of the meshing gear, and meshing and tooth beating are prevented when the meshing gear and the rotor are asynchronous; when in synchronization, the friction torque disappears, and the torque of the drive plate drives the rotor and the synchronous ring to move forward by half of the teeth to be smoothly meshed.

When meshing, the sliding block 20 is matched with the spline and enters the inside of the meshing gear; the slider 20 is fitted with the synchronizing ring 21 through a groove, and the synchronizing ring 21 is rotated in unison with the meshing gear 6.

During braking, the power driving structure 4 pushes the meshing gear 6 backwards, the meshing gear 6 drives the synchronous ring to be close to the rotor 7, and the sliding block 20 can slide relative to the spline hub 18 and does not leave a positioning position; when the friction conical surface of the synchronizing ring 21 is contacted with the friction conical surface of the rotor 7, a reverse moment is formed, so that the right end tooth conical surface of the meshing gear 6 is opposite to the end tooth conical surface of the synchronizing ring 21 to be locked, and the synchronizing ring 21 is pressed towards the rotor 7; when the friction torque of the friction conical surface is gradually increased to the point that the rotor 7 is synchronous with the meshing gear 6, the friction torque gradually disappears, and the clockwise drive plate torque can drive the synchronous ring 21 forwards to be smoothly meshed; after meshing, corresponding media are supplied to the working cavity to generate corresponding braking force.

When no load is carried, the spline hub 18 and the meshing gear 6 rotate together; the outer circle of the sliding block 20 is provided with a bulge which is matched and positioned with a circular groove at the internal spline of the meshing gear 6, and the synchronizing ring 21 is arranged outside the left end surface of the meshing gear 6; the rotor does not rotate with the retarder shaft 1, the meshing gear 6 rotates with the retarder shaft 1, and the meshing gear 6 is disengaged from the meshing teeth of the rotor under the action of the separation spring 13 and returns to the limiting position at the front end; the working cavity of the stator and the rotor only has a small amount of medium.

The utility model discloses second embodiment power drive structure 4 is the cylinder.

Claims (2)

1. A rotor detachable hydraulic retarder is characterized in that: the retarder comprises a retarder shaft, an end face bearing, an end cover, a power driving structure, a rotor, a stator, a body, a rear end cover, a bearing bracket, a rear bearing, a working cavity oil seal, a front oil seal and a gear shifting separation structure; the front bearing is arranged and installed behind the power input gear and is embedded at the left side of the end cover; the rear bearing outer sleeve is embedded on the bearing support; the rotor is axially positioned with the stator through the end face bearing, the stator inner hole and the positioning snap ring; the stator, the end cover and the body form circumferential and axial positioning; the power driving structure and the annular end face bearing are arranged in an annular cylinder body of the end cover, and the power driving structure is an annular piston; the retarder shaft is connected with the power driving structure in a torsion-resistant manner through a spline; the gear shifting separation structure comprises an engaging gear, a separation spring and a synchronous ring; the right end of the separating spring seat is arranged on a shaft shoulder of the retarder shaft, and the left side of the separating spring seat acts on the meshing gear; the synchronizing ring is arranged behind the meshing gear, and the outer friction conical surface of the synchronizing ring is matched with the inner friction conical surface of the rotor.

2. A rotor-separable hydrodynamic retarder according to claim 1, characterized in that: the gear separation structure also comprises a synchronous locking ring, a bearing, an elastic snap ring, a spline hub, a spring ring and a sliding block; the annular piston is always contacted with the meshing gear through the end face bearing, so that the annular piston does not rotate along with the meshing gear; the slide block is arranged in the groove of the spline hub; the sliding block is matched with the groove on the spline hub and can slide left and right; meanwhile, the sliding block is matched with the groove of the synchronous ring; the excircle of the sliding block is provided with an annular bulge which is matched with an annular groove of an internal spline of the meshing gear; the meshing gear is connected with a retarder shaft to transmit braking torque; the rotor shaft sleeve is supported on the excircle of the meshing gear shaft sleeve through a bearing, so that the meshing gear can conveniently slide left and right on the retarder shaft; the spring ring is pressed on the inner teeth of the meshing gear; the spline hub is matched with the bearing to rotate; the inner hole of the spline hub is matched with a small shaft shoulder protruding from the rotor, one end of the elastic clamping ring is embedded on the rotor, and the other end of the elastic clamping ring compresses the spline hub to enable the spline hub to be static relative to the axial direction of the rotor.

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