CN111075868A - Rotor detachable hydraulic retarder - Google Patents
Rotor detachable hydraulic retarder Download PDFInfo
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- CN111075868A CN111075868A CN202010109631.2A CN202010109631A CN111075868A CN 111075868 A CN111075868 A CN 111075868A CN 202010109631 A CN202010109631 A CN 202010109631A CN 111075868 A CN111075868 A CN 111075868A
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- 238000000926 separation method Methods 0.000 claims abstract description 31
- 230000009471 action Effects 0.000 claims abstract description 7
- 230000001360 synchronised effect Effects 0.000 claims description 36
- 239000003921 oil Substances 0.000 claims description 31
- 238000007789 sealing Methods 0.000 claims description 11
- 230000002441 reversible effect Effects 0.000 claims description 9
- 230000000670 limiting effect Effects 0.000 claims description 6
- 238000010009 beating Methods 0.000 claims description 3
- 239000000110 cooling liquid Substances 0.000 claims description 3
- 239000007788 liquid Substances 0.000 claims description 3
- 230000001050 lubricating effect Effects 0.000 claims description 3
- 239000010687 lubricating oil Substances 0.000 claims description 3
- 230000003068 static effect Effects 0.000 claims description 3
- 230000001502 supplementing effect Effects 0.000 claims description 3
- 230000000694 effects Effects 0.000 claims description 2
- 238000000034 method Methods 0.000 claims 8
- 230000002829 reductive effect Effects 0.000 abstract description 8
- 239000010720 hydraulic oil Substances 0.000 description 2
- 239000010727 cylinder oil Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
- F16D67/02—Clutch-brake combinations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D57/00—Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention discloses a hydraulic retarder with a separable rotor; the retarder shaft is connected with the power driving structure; 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; the retarder shaft rotates when the vehicle runs normally and is unloaded; when the brake is released, the driving force is removed, the meshed gear is separated from the rotor under the action of the separation spring and returns to the left side positioning position, and the rotor does not rotate with the retarder shaft any more and runs in no-load; the invention arranges the integral separable rotor 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 invention has stable operation, high space interest rate, compact structure, reasonable stress, effectively reduced stress of the meshing gear and effectively controlled component weight. 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
Technical Field
The invention belongs to the technical field of automobile engineering, and relates to a hydraulic retarder with a separable rotor.
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 invention discloses a hydraulic retarder with a separable rotor, which aims to solve the problems that the hydraulic retarder in the prior art has large no-load loss and the like.
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 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.
According to an optimized scheme, the gear shifting separation structure further 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 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.
According to an optimized scheme, the meshing gear is in a butterfly shape and is connected with the retarder shaft through a spline.
According to an optimized scheme, the number of the sliding blocks of the gear shifting separation structure is more than or equal to two, the spline hub is provided with circumferentially uniformly distributed grooves with the number equal to that of the sliding blocks, the sliding blocks are arranged in the uniformly distributed grooves of the spline hub, and the sliding blocks are matched with the uniformly distributed grooves of the synchronizing ring.
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 invention has the positive effects that: 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 an enlarged partial 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
Embodiments of the present invention are described in detail below with reference to the accompanying drawings.
The first embodiment of the invention is shown in fig. 1 and fig. 2, and comprises 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 support 11, a rear bearing 12, a working cavity 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 second embodiment power drive mechanism 4 of the present invention is a cylinder.
Claims (8)
1. A hydraulic retarder with a separable rotor; the method 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 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.
2. A rotor separable hydrodynamic retarder according to claim 1; the method is characterized in that: the gear shifting 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 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.
3. A rotor separable hydrodynamic retarder according to claim 2; the method is characterized in that: when meshing, the sliding block and the spline are matched and enter the meshing gear; the slide block is matched with the synchronous ring through the groove, and the synchronous 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, supplying corresponding media 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.
4. A rotor separable hydrodynamic retarder according to claim 2; the method is characterized in that: 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.
5. A rotor separable hydrodynamic retarder according to claim 2; the method is characterized in that: the number of the sliding blocks of the gear shifting separation structure is more than or equal to two, the spline hub is provided with circumferentially uniformly distributed grooves with the same number as the sliding blocks, the sliding blocks are arranged in the uniformly distributed grooves of the spline hub, and the sliding blocks are matched with the uniformly distributed grooves of the synchronizing ring.
6. A rotor separable hydrodynamic retarder according to claim 2, claim 5; the method is characterized in that: the three sliders are arranged in three uniformly distributed grooves of the spline hub.
7. A rotor separable hydrodynamic retarder according to claim 2; the method is characterized in that: 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.
8. A rotor separable hydrodynamic retarder according to claim 2; the method is characterized in that: the meshing gear is in a butterfly shape and is connected with the retarder shaft through a spline.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010109631.2A CN111075868A (en) | 2020-02-22 | 2020-02-22 | Rotor detachable hydraulic retarder |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010109631.2A CN111075868A (en) | 2020-02-22 | 2020-02-22 | Rotor detachable hydraulic retarder |
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| Publication Number | Publication Date |
|---|---|
| CN111075868A true CN111075868A (en) | 2020-04-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010109631.2A Pending CN111075868A (en) | 2020-02-22 | 2020-02-22 | Rotor detachable hydraulic retarder |
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| CN (1) | CN111075868A (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4846316A (en) * | 1987-04-15 | 1989-07-11 | Akebono Brake Industry Co., Ltd. | Hydraulic retarder attached with parking brake |
| CN204239536U (en) * | 2014-11-28 | 2015-04-01 | 宁波华盛汽车部件有限公司 | The drive mechanism of hydrodynamic retarder |
| CN105992894A (en) * | 2014-02-10 | 2016-10-05 | 福伊特专利有限公司 | Hydrodynamic retarder |
| CN106931057A (en) * | 2017-03-23 | 2017-07-07 | 陕西法士特齿轮有限责任公司 | A kind of separable Retarder work cavity configuration of rotor |
| CN208204016U (en) * | 2018-05-07 | 2018-12-07 | 洛阳茵特汽车配件有限公司 | A kind of self-compensation type Retarder movable sealing structure |
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2020
- 2020-02-22 CN CN202010109631.2A patent/CN111075868A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4846316A (en) * | 1987-04-15 | 1989-07-11 | Akebono Brake Industry Co., Ltd. | Hydraulic retarder attached with parking brake |
| CN105992894A (en) * | 2014-02-10 | 2016-10-05 | 福伊特专利有限公司 | Hydrodynamic retarder |
| CN204239536U (en) * | 2014-11-28 | 2015-04-01 | 宁波华盛汽车部件有限公司 | The drive mechanism of hydrodynamic retarder |
| CN106931057A (en) * | 2017-03-23 | 2017-07-07 | 陕西法士特齿轮有限责任公司 | A kind of separable Retarder work cavity configuration of rotor |
| CN208204016U (en) * | 2018-05-07 | 2018-12-07 | 洛阳茵特汽车配件有限公司 | A kind of self-compensation type Retarder movable sealing structure |
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