CN111043198A - Stator preposed hydrodynamic retarder - Google Patents
Stator preposed hydrodynamic retarder Download PDFInfo
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- CN111043198A CN111043198A CN202010109626.1A CN202010109626A CN111043198A CN 111043198 A CN111043198 A CN 111043198A CN 202010109626 A CN202010109626 A CN 202010109626A CN 111043198 A CN111043198 A CN 111043198A
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- 230000001360 synchronised effect Effects 0.000 claims abstract description 98
- 238000007789 sealing Methods 0.000 claims abstract description 38
- 238000000926 separation method Methods 0.000 claims abstract description 20
- 239000003921 oil Substances 0.000 claims description 139
- 239000010687 lubricating oil Substances 0.000 claims description 5
- 239000010724 circulating oil Substances 0.000 claims description 3
- 230000000694 effects Effects 0.000 claims description 3
- 230000001502 supplementing effect Effects 0.000 claims description 3
- 230000003068 static effect Effects 0.000 claims description 2
- 238000000034 method Methods 0.000 claims 8
- 230000005540 biological transmission Effects 0.000 abstract description 4
- 239000010720 hydraulic oil Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 206010039203 Road traffic accident Diseases 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 239000000110 cooling liquid Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005562 fading Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
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Classifications
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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
-
- 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
- F16D65/00—Parts or details
- F16D65/78—Features relating to cooling
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0413—Controlled cooling or heating of lubricant; Temperature control therefor
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/045—Lubricant storage reservoirs, e.g. reservoirs in addition to a gear sump for collecting lubricant in the upper part of a gear case
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0457—Splash lubrication
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0469—Bearings or seals
- F16H57/0471—Bearing
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0469—Bearings or seals
- F16H57/0472—Seals
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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
- F16D2300/00—Special features for couplings or clutches
- F16D2300/02—Overheat protection, i.e. means for protection against overheating
- F16D2300/021—Cooling features not provided for in group F16D13/72 or F16D25/123, e.g. heat transfer details
- F16D2300/0214—Oil or fluid cooling
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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
- F16D65/00—Parts or details
- F16D65/0006—Noise or vibration control
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
The invention discloses a stator preposed hydrodynamic retarder; the retarder comprises a retarder shaft, a front bearing, a stator, a rotor, a stator end cover, a body, a separation spring, an annular piston, a meshing gear, a locking sliding framework, a return spring, a synchronous locking ring, a needle bearing, an outer oil seal and the like; the stator and the stator end cover seal a high-pressure oil outlet cavity B and seal a low-pressure oil inlet cavity A by the retarder shaft; the stator is arranged in front, and the rotor is arranged behind the stator and in a closed cavity in the body; a sealing ring is arranged between the rotor and the stator and used for isolating the working cavity C from the oil inlet cavity A; when the rotor does not rotate, the engaging gear is pushed to move rightwards by the separating spring until the right positioning dead point, and meanwhile, the engaging gear is separated from the rotor, so that the rotor does not rotate relative to the shaft, and no idle load loss is caused even though a small amount of medium is stored in the working cavity C; the oil duct is arranged in the front of the stator, so that the radial size is reduced, and the interference with a transmission shaft is avoided; the weight is reduced to the maximum extent, the noise is reduced, the strength and the reliability are improved, and the no-load loss is reduced.
Description
Technical Field
The invention belongs to the technical field of automobile engineering, and relates to a hydraulic retarder with a preposed stator, in particular to a hydraulic retarder with a preposed stator and a rear separable rotor; the device is particularly suitable for the anti-torsion connection of the input gear of the parallel retarder and the retarder shaft behind the gearbox of the passenger car and the truck.
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.
If the automobile is in turning and descending, the speed is too high to cause traffic accidents easily, and the long-time frequent use of the service brake not only causes serious abrasion, but also more importantly, the brake is overheated, even the brake fails due to serious heat fading of the brake, even the serious consequence of fire catching is caused, so that a non-contact and active heat dissipation device such as a retarder and the like is needed to decelerate or control the speed when the automobile descends a long slope. Although there are various auxiliary brakes such as exhaust brake, it is difficult to completely satisfy the requirement of safe control speed. Therefore, the heavy truck or bus which is commonly recognized in the industry at home and abroad is best matched with a hydraulic retarder which can meet the requirements.
At present, a general hydrodynamic retarder adopts a front rotor.
And passenger train, the rearmounted retarber power input of truck gearbox connects in parallel has two kinds of situations:
an input gear and a retarder shaft are supported by a bearing, the gear is connected with the shaft in a non-torsion-resistant manner, namely the retarder shaft does not rotate with a transmission shaft when in no load; the retarder shaft is connected with the rotor in a torsion-resistant mode, or is connected with the rotor in a meshing mode in a braking mode through other modes, and power is combined with the rotor in the braking mode, so that no-load loss of the retarder is reduced.
The other is that the gear of the output shaft of the gearbox is meshed with the input gear of the retarder, if the input gear of the retarder is connected with the retarder shaft in a torsion-resistant manner, such as spline connection, the retarder shaft rotates along with the running of the vehicle; the vehicle normally runs, and is called as a retarder no-load when not braking; in order to reduce the no-load loss of the retarder, the rotor and the shaft are supported by the bearing, and power is transmitted to the rotor through meshing of the meshing structure during braking to realize braking.
Disclosure of Invention
The invention discloses a hydraulic retarder with a front stator, which aims to solve the problems that in the prior art, the torque of the retarder is small, no-load loss is caused when an input gear of the retarder is connected with a retarder shaft in an anti-torsion mode, and the spatial arrangement of the rear hydraulic retarder in parallel connection of a gearbox of a passenger car and a truck is difficult.
The invention comprises a retarder shaft, a front bearing, a stator, a rotor, a stator end cover, a body, a separation spring, an annular piston, a meshing gear, a locking sliding framework, a return spring, a synchronous locking ring, a needle bearing, an outer oil seal, an oil inlet cavity A, an oil outlet cavity B, a working cavity C, an output oil duct D and an oil return duct E; the stator and the stator end cover seal a high-pressure oil outlet cavity B and seal a low-pressure oil inlet cavity A by the retarder shaft; the stator is arranged in front, and the rotor is arranged behind the stator and in a closed cavity in the body; a sealing ring is arranged between the rotor and the stator and used for isolating the working cavity C from the oil inlet cavity A; the inner hole of the rotor is provided with a sealing ring to prevent the oil supply cavity of the rotor from being communicated with the oil inlet cavity A of the stator; the meshing gear is arranged behind the rotor, and the separating spring seat and the end face bearing are arranged between the separating spring and the rotor to ensure relative movement; the rotor is always positioned at the front end positioning position under the action of the spring, and when the annular piston does not apply force, the meshing gear is separated from the rotor, so that the meshing gear returns to the right side positioning position; the locking sliding framework is matched with a spline of the meshing gear and can slide left and right in the meshing gear, so that the separation of a friction conical surface of the synchronous locking ring and the rotor is ensured, and the left side of the synchronous locking ring is limited by a positioning pin; the return spring is positioned between the meshing gear and the sliding framework to ensure that the sliding block and the synchronous ring return to a left dead point when in no-load, and ensure that the synchronous locking ring is positioned at the outer end of the meshing gear teeth when in no-load and a certain gap is ensured; the rotor meshing teeth are arranged on the right side of the rotor; the meshing teeth of the rotor are meshed with the meshing gear, the rotor starts to rotate, then a proper amount of medium in the oil storage cavity is conveyed into the working cavity C according to requirements, the rotor rotates relative to the stator, the medium is pushed to the stator through centrifugal action, the medium moving at high speed is blocked by the stator, and corresponding braking force can be generated to realize braking; when the synchronous locking mechanism is separated, working media in the working cavity are removed, compressed air or hydraulic pressure in the annular piston is withdrawn, and under the action of a separating spring and a locking sliding framework return spring, a separating acting force is generated, so that the meshing gear moves rightwards to drive the framework and the synchronous locking ring to move rightwards until meshing is relieved, and the synchronous locking ring is separated from the right end face of the rotor; when the rotor does not rotate, the meshing gear is pushed to move rightwards by the separating spring until the right positioning dead point, and meanwhile, the meshing gear is separated from the rotor, so that the rotor does not rotate relative to the shaft, and no idle load loss is caused even though a small amount of medium is stored in the working cavity C.
A clamping ring is arranged on the left side of the locking sliding framework, so that the gap between the synchronous locking ring and the rotor friction conical surface is ensured; the rotor and the retarder shaft are supported through a needle bearing; when the vehicle is normally driven, the retarder shaft rotates, and the rotor is still; the meshing teeth and the meshing gear of the rotor are connected with the retarder shaft in a torsional mode through a spline and can slide left and right on the shaft spline; spline teeth are arranged on the back of the rotor, the right end of each spline tooth is in a conical shape, and the guide meshing gear is smoothly meshed with an external spline of the rotor to generate synchronous driving plate torque; the power is smoothly meshed and transmitted by the retarder shaft through the meshing gear and the synchronous locking ring; the meshing gear is meshed with the rotor and then integrally and jointly rotates with the rotor; the space behind the rotor is provided with a separation meshing and executing structure; the integral separable rotor is arranged at the rear, the right side of the rotor and the body jointly form an oil cavity, the oil cavity is communicated with the circulating oil duct through an oil hole, the oil cavity is just started to work as an oil supplementing hole, and when air in the cavity is removed, the oil cavity is used as an output port; the stator end cover, the front bearing and the outer oil seal gearbox lubricating oil; the medium flowing out of the heat exchanger enters an oil return passage E of the working cavity C; the oil enters a stator end cover through an oil return passage E and forms a stator oil inlet cavity A with the axis close to the stator, and enters a working cavity C formed by the stator and the rotor through a blade oil port of the stator close to the axis; when braking, the right side of the annular piston is communicated with compressed air or hydraulic pressure, the piston moves leftwards, the meshing gear moves leftwards under the pushing of the annular piston, the meshing gear is meshed with the rear external teeth of the rotor under the pushing of the execution piston to form a rotor which integrally rotates, and the rotor is stably pushed to the left positioning position; the locking framework moves leftwards simultaneously under the action of the spring force; when the outer conical surface of the synchronous locking ring is contacted with the inner conical surface of the inner hole of the rotor, a reverse friction torque is generated, so that the synchronous locking ring rotates reversely, the end tooth conical surface of the synchronous ring is ensured to be opposite to the end tooth conical surface of the meshing gear to be locked, and when the rotor and the meshing gear are synchronous, the rotor rotates forwards by half a tooth by the driving plate torque generated by the end tooth conical surface to realize smooth meshing; the output oil duct D of the working cavity C adopts a circuitous oil duct to increase resistance; and the oil return passage E adopts a large-diameter oil passage to reduce oil return resistance.
The output oil duct D of the working cavity C adopts a circuitous oil duct to increase resistance; and the oil return passage E adopts a large-diameter oil passage to reduce oil return resistance.
The invention also comprises a synchronous locking ring snap ring, a rotor needle bearing positioning ring, a rotor positioning ring, an end face bearing, an annular end face bearing, a rear bearing, an end face bearing of a meshing gear, an end face bearing, an input gear and an end face bearing of a separating spring seat; the front end of the rotor is axially positioned through an end face bearing and a shaft shoulder, and a needle bearing positioning ring and a rotor needle bearing are arranged in a rotor inner hole to ensure that the shaft and the rotor can relatively rotate at a high speed; at the front end of a retarder with power input, a stator is axially positioned through a stator end cover; the retarder shaft is positioned with the front bearing through the space between the platforms; the rotor is axially positioned through a shaft shoulder at the front end of the rotor and an end face bearing and is pushed to a left positioning point under the action of a separation spring all the time; the left side of the end face bearing leans against a shaft shoulder to carry out left side axial positioning, so that the stability of the rotor during rotation and the clearance between the rotor and the stator are ensured; the right side is pressed to the left side positioning position by a spring through an end face bearing spring seat; the right side of the meshing gear is positioned on the rear bearing inner sleeve through an end face bearing, and the rotor and the retarder shaft are supported through a needle bearing; the axial positioning ensures the clearance and the related precision between the stator and the rotor; adjusting a fastening adjusting bolt of the inner ring of the rear bearing, and adjusting and loosening a gap between the front bearing and the rear bearing; the noise of the bearing and the like during movement is reduced, and the gap of the stator and the rotor during braking is ensured, so that the realization of the maximum braking torque is ensured; when the locking sliding framework is in no-load, the locking sliding framework is limited at a left dead point under the action of a return spring; ensuring that the synchronous locking ring is positioned at the outer end of the meshing gear teeth when in no-load and ensuring a certain gap; the meshed gear and the shaft rotate simultaneously, and the framework can not only transmit torque but also rotate together with the shaft due to the matching of the external spline and the internal tooth of the meshed gear, so that the synchronous locking ring is driven to rotate simultaneously; skeleton axle sleeve left side accessible snap ring location when avoiding synchronous lock ring to drop, guarantees that synchronous lock ring and rotor internal spline right-hand member leave 1mm at least clearance, contact friction when avoiding empty load. Meanwhile, the synchronous locking ring and the right side of the locking sliding framework groove are limited, and when the framework is positioned at the leftmost side, the gap between the right tooth end of the external spline of the synchronous locking ring and the left tooth end of the meshing gear is at least 1 mm; locking slip skeleton, synchronous lock ring, return spring, meshing gear, annular piston, separation spring, can realize smooth-going meshing and reliable separation.
When the synchronous locking device is braked, the meshing gear drives the synchronous ring to move left together under the pushing of the annular piston, when the outer friction conical surface of the synchronous ring is just contacted with the inner friction conical surface of the rotor, the synchronous ring reversely rotates by an angle, so that the conical surface of the spline tooth end of the meshing gear is ensured to be opposite to the conical surface of the right tooth end of the synchronous locking ring, and the effect of locking the meshing gear and the synchronous locking ring is achieved, thus under the action of the pushing force, the friction conical surface of the synchronous locking ring is completely attached to the friction conical surface of the inner hole of the rotor, the maximum friction torque is generated, and the rotor is driven to rotate; after synchronization, the poking force disc moment is larger than the friction moment, the synchronous locking ring and the rotor and the meshing gear can be poked to rotate forwards for an angle in the same direction until the meshing gear is smoothly meshed with the external spline of the synchronous locking ring, and the right end face of the rotor spline is provided with the same conical surface; at the moment, the synchronous locking ring and the external spline of the framework slide to the right in the internal spline of the meshing gear at the same time; under the action of actuating pressure, the meshing gear is meshed with the external teeth at the back of the rotor to form an integral rotor which rotates together.
According to an optimized scheme of the invention, 3 grooves are uniformly distributed at the shaft hole of the locking sliding framework and matched with three 120-degree uniformly distributed inner teeth on the shaft hole of the synchronous locking ring sleeved outside, and the grooves are wider than teeth; the locking sliding framework outer splines matched with the driving meshing gear inner splines can slide left and right in the meshing gear, and three positioning pins are uniformly distributed at 120 degrees on the meshing gear; one tooth is removed from the position of the positioning pin of the internal spline of the meshing gear, the outer diameter of the positioning pin is smaller than the tooth width, so that the left position of the sliding framework can be limited and locked, and the sliding framework can slide rightwards; 3 grooves are evenly distributed in the locking sliding framework shaft hole, and are matched with three inner teeth which are sleeved on the synchronous locking ring shaft hole at 120 degrees and are evenly distributed, but the grooves are at least 2 teeth wide.
The optimized scheme of the invention also comprises an annular piston oil seal, a stator inner hole sealing ring, a stator input/output cavity sealing ring, a rotor sealing ring, an annular piston double sealing element, an oil return channel sealing element, an inner oil seal and a pressure reducing ring; the inner oil seal seals a retarder medium, and the pressure reducing ring reduces the impact of the pressure of the medium on the oil seal; 2 sealing rings are arranged on the excircle of the stator and are used for sealing the end cover and the body, and the input cavity and the output cavity of the stator are separated and isolated by the sealing rings; the right side of the annular piston can be communicated with compressed air or liquid pressure to generate meshing thrust; the annular piston can move left and right in the annular piston cylinder body in the body by contacting the end face bearing with the meshing gear, and an annular piston oil seal, an annular piston sealing ring or an oil seal sealing medium mutually leak; the outer ring of the rear bearing is fixed on the body, and the right side of the outer ring of the rear bearing is isolated from the oil storage cavity of the body by a bearing end cover; a lubricating oil storage cavity is formed between the rear bearing and the sealing end cover, is communicated with the rear cavity of the rotor, is in lubricating communication with the oil seal of the front gearbox, and simultaneously lubricates the rear bearing; the outer end of the meshing gear is distributed with a plurality of uniformly distributed outer teeth which are used for carrying out splash lubrication on the ring-shaped piston end surface bearing, the right end surface bearing of the meshing gear, the rear bearing and other related high-speed rotating parts in no-load; at least one third of medium is always remained in an oil cavity formed by the right side of the rotor and the body together, the meshing and separating mechanism is arranged in the cavity, blades are uniformly distributed on the excircle of the meshing gear, splashing is formed during rotation, and the end face bearing is lubricated. An oil cavity formed by the right side of the rotor and the body simultaneously leads to a closed cavity formed by the right side of the rear bearing and the small end cover through a small hole; the bearing fastening bolt is provided with a central hole and directly leads to the space between the left outer oil seal and the inner oil seal to lubricate the sealing lip of the oil seal; an oil cavity formed by a rear bearing communicated with the rear cavity of the rotor and a bearing sealing end cover is used for lubricating two oil seal sealing lips arranged on the front bearing and the rear bearing.
The invention also comprises an output temperature sensor and a working cavity input oil temperature sensor, wherein the kinetic energy of the rotor rotation in the working cavity is converted into the heat of a medium, and then enters a heat exchanger through an output oil duct D to exchange the heat; two temperature sensors and a temperature sensor are arranged on the outer side of the stator end cover and used for respectively monitoring the temperature of the medium entering and exiting the working cavity C.
During braking, the meshed rotor rotates relative to the stator, working medium in the oil storage cavity is pressed into the oil return channel E according to gear requirements to enter the stator oil inlet cavity A and further enter the working cavity C, the medium is thrown to the outer end of the stator under the centrifugal action of the rotor, flows into the stator oil outlet cavity B through the stator outer edge output port, enters the heat exchanger through the output oil duct D, and exchanges heat with engine cooling liquid flowing through the other channel of the heat exchanger. The cooled medium flows out of the heat exchanger, enters an oil return passage E, flows into an oil inlet cavity A of the stator and enters a working cavity C of the stator and the rotor; the kinetic energy of the vehicle is changed into the kinetic energy of the medium from the rotation of the rotor, and then the kinetic energy is converted into heat through the circulation of the medium and the resistance of the stator, and the heat is dissipated into the air through heat exchange.
In an optimized scheme, the annular piston shell is arranged on the retarder body or embedded on the retarder body; the compressed air or hydraulic pressure of the execution ring-shaped piston is controlled by valves such as a 3-position 2-way valve and the like; the annular execution piston with compressed air or hydraulic pressure as a power source adopts an end face bearing on the contact surface between the movement and the possible rest, so that the noise and the resistance are reduced, and the reliability is ensured.
The invention has the positive effects that: the oil duct is arranged in the front of the stator, so that the radial size is reduced, and the interference with a transmission shaft is avoided. The weight is reduced to the maximum extent, the noise is reduced, the strength and the reliability are improved, and the no-load loss is reduced. The retarder torque is favorably improved, and the maximum braking torque can reach 4500Nm or even 5000 Nm.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic oil return diagram of the present invention;
FIG. 3 is a schematic view of a synchronizer ring mounting structure according to the present invention;
in the figure: 1 retarder shaft, 2 front bearings, 3 stators, 4 rotors, 5 stator end covers, 6 bodies, 7 stator sealing rings, 8 rotor sealing rings, 9 annular piston oil seals, 10 annular pistons, 11 annular end face bearings, 12 annular piston double seals, 13 rear bearings, 14 separating springs, 15 meshed gear end face bearings, 16 locked sliding framework return springs, 17 meshed gears, 18 locked sliding frameworks, 19 synchronous locking ring snap rings, 20 end face bearings, 21 synchronous locking rings, 22 rotor needle bearings, 23 rotor needle bearing positioning rings, 24 oil return channel seals, 25 rotor sealing rings, 26 rotor positioning rings and end face bearings, 27 output temperature sensors, 28 working cavity input oil temperature sensors, 29 stator input and output cavity sealing rings, 30 pressure reducing rings, 31 inner oil seals, 32 outer oil seals, 33 input gears, 34 stator inner hole sealing rings, 35 separating spring seat end face bearings, The oil inlet cavity A, the oil outlet cavity B, the working cavity C, the output oil duct D, the oil return channel E and the compressed air or hydraulic oil inflow channel F.
Detailed Description
An embodiment of the present invention is described in detail below with reference to the accompanying drawings.
The embodiment of the invention is shown in fig. 1, fig. 2 and fig. 3, and comprises a retarder shaft 1, a front bearing 2, a stator 3, a rotor 4, a stator end cover 5, a body 6, a stator sealing ring 7, a rotor sealing ring 8, an annular piston oil seal 9, an annular meshing piston 10, an annular end face bearing 11, an annular piston double sealing element 12, a rear bearing 13, a separation spring 14, an active meshing gear end face bearing 15, a locking sliding framework return spring 16, a meshing gear 17, a locking sliding framework 18, a synchronous locking ring snap ring 19, an end face bearing 20, a synchronous locking ring 21, a rotor needle bearing 22, a rotor needle bearing positioning ring 23, an oil return channel sealing element 24, a rotor sealing ring 25, a rotor positioning ring and end face bearing 26, an output temperature sensor 27, a working chamber input sensor 28, a stator input and output chamber sealing ring 29, a pressure reducing ring 30, an, The oil-sealed separating device comprises an outer oil seal 32, an input gear 33, a stator inner hole sealing ring 34, a separating spring seat end face bearing 35, an oil inlet cavity A, an oil outlet cavity B, a working cavity C, an output oil duct D and an oil return duct E; the rotor 4 is behind the stator and in a closed cavity in the body 6, the stator 3 is arranged in front, the front end of the rotor is axially positioned through an end face bearing 26 and a shaft shoulder, and the outer circle of a rotor shaft sleeve and an inner hole of the stator are provided with sealing rings 34 for isolating a working cavity C from an oil inlet cavity A; the rotor inner hole is provided with a sealing ring 25 to prevent the rotor oil supply cavity from being communicated with the stator oil inlet cavity A, and the rotor inner hole is provided with a needle bearing positioning ring 23 and a rotor needle bearing 22 to ensure that the shaft and the rotor can relatively rotate at high speed; the separating spring seat and the end face bearing 35 are arranged between the separating spring 14 and the rotor 4 to ensure relative movement, the rotor is always positioned at the front end positioning position under the action of the spring, and when the annular piston does not apply force, the meshing gear 17 is separated from the rotor 4 to return the meshing gear to the right side positioning position; the locking sliding framework 18 is matched with the internal spline of the driving meshing gear 17 through an external spline, and a positioning pin is arranged on the left side to prevent the locking sliding framework from sliding out and ensure that the friction conical surface of the synchronizing ring 19 is separated from the rotor and can slide left and right in the meshing gear. The return spring 16 is positioned between the meshing gear 17 and the sliding framework 18 to ensure that the slide block and the synchronous ring return to a left dead center when in no-load, and ensure that the synchronous locking ring 19 is positioned at the outer end of the meshing gear teeth when in no-load and a certain gap is ensured. 3 grooves are uniformly distributed in the position of the 18 shaft holes of the locking sliding framework and are matched with three inner teeth which are uniformly distributed at 120 degrees on the shaft holes of the synchronous locking ring sleeved outside, and the grooves are wider than teeth. The left side of the framework shaft sleeve is synchronously locked through a clamping ring, so that the synchronous locking ring and the clearance of the rotor friction conical surface are ensured while the synchronous locking ring is prevented from falling off; the meshing teeth of the rotor 4 are arranged on the right side of the rotor 4; the rotor 4 and the retarder shaft 1 are supported through a needle bearing 22, the retarder shaft 1 rotates during normal driving, and the rotor 4 is stationary; the meshing teeth of the rotor and the meshing gear 17 are connected with the retarder shaft 1 in a torsional mode through a spline and can slide left and right on the shaft spline; the back of the rotor is directly provided with a spline tooth, and the right end of the tooth is conical so as to generate synchronous driving plate torque and guide the meshing gear 17 to smoothly mesh with the external spline of the rotor 4; the power is smoothly meshed and transmitted by the retarder shaft 1 through the meshing gear 17 and the synchronous locking ring; the meshing structure is arranged behind the rotor and is meshed with the rotor to form an integral body to rotate together; the space behind the rotor 4 is provided with a separate meshing and actuating structure.
The locking sliding framework outer splines matched with the inner splines of the meshing gear 17 can slide left and right in the meshing gear, and three positioning pins are uniformly distributed at 120 degrees on the meshing gear; one tooth is removed from the position of the positioning pin of the internal spline of the meshing gear, the outer diameter of the positioning pin is smaller than the tooth width, so that the left position of the sliding framework can be limited and locked, and the sliding framework can slide rightwards; 3 grooves of locking slip skeleton shaft hole department equipartition, with the three internal tooth cooperations of the 120 ° equipartition of cover on the synchronous lock ring shaft hole in outside, nevertheless the groove is 1 tooth than the tooth width at least, also can guarantee that synchronizer ring and skeleton rotate along with the meshing gear simultaneously. When the vehicle is unloaded, the locking sliding framework is limited at a left dead point under the action of the return spring 16; ensuring that the synchronizing locking ring 19 is at the outer end of the meshing gear teeth when no load exists and ensuring that a certain gap exists; the meshed gear and the shaft rotate simultaneously, and the framework can not only transmit torque but also rotate together with the shaft due to the matching of the external spline and the internal tooth of the meshed gear, so that the synchronous locking ring is driven to rotate simultaneously; the accessible snap ring location in skeleton axle sleeve left side avoids synchronous lock ring to drop in, guarantees the clearance of synchronous lock ring and rotor internal spline right-hand member, avoids contact friction when empty load. Meanwhile, the synchronous locking ring is limited with the right side of the locking sliding framework groove, and when the framework is positioned at the leftmost side, the gap between the right tooth end of the external spline of the synchronous locking ring and the left tooth end of the meshing gear is reserved; the locking sliding framework 18, the synchronous locking ring 19, the return spring 14, the meshing gear 17, the annular piston 10 and the separating spring 14 can realize smooth meshing and reliable separation.
When meshing, the meshing gear drives the framework 18 and the synchronizing ring 19 to move left, and after the outer conical surface of the synchronizing locking ring is contacted with the inner conical surface of the inner hole of the rotor, a reverse friction torque is generated, so that the synchronizing locking ring rotates reversely by an angle to play a role in meshing the locking meshing gear with the synchronizing locking ring. The synchronous locking ring 19, the locking sliding framework 18, the locking sliding framework return spring 16, the meshing gear 17, the separation spring 14 and the like guarantee smooth meshing and reliable separation.
At the front end of a retarder with power input, a stator 3 is axially positioned through a stator end cover 5; the retarder shaft 1 is positioned with the front bearing 2 through the space between the tables; the rotor 4 is axially positioned through a shaft shoulder at the front end of the rotor 4 and an end face bearing 26 and is always pushed to a left positioning point under the action of the separation spring 14; the left side of the end face bearing 23 leans against a shaft shoulder to carry out left side axial positioning, so that the stability of the rotor during rotation and the clearance between the rotor and the stator are ensured; the right side is pressed to the left side positioning position by a spring through an end face bearing spring seat; the right side of the meshing gear 17 is positioned on the rear bearing inner sleeve through an end face bearing 15, and the rotor 4 and the retarder shaft 1 are supported through a needle bearing 22; the axial positioning ensures the clearance and the related precision between the stator and the rotor; adjusting the fastening adjusting bolt of the inner ring of the rear bearing 13, and adjusting and loosening the gap between the front bearing and the rear bearing; the noise of the bearing and the like during movement is reduced, and the gap of the stator and the rotor during braking is ensured, so that the realization of the maximum braking torque is ensured.
The front bearing and the rear bearing ensure that the shaft reduces noise and resistance when rotating at a high speed, the two oil seals behind the front bearing are used for preventing engine oil of the isolated speed changing box from leaking into the speed reducing device, and the rear oil seal is used for preventing medium of the speed reducing device from leaking or being in oil connection with the speed changing box.
A stator oil inlet cavity A is sealed between the stator 3 and the stator end cover 5; an oil outlet cavity B; the stator 3 is arranged in front, so that the radial size is reduced, and the interference with a transmission shaft is avoided; the integral separable rotor 4 is arranged at the rear part, and the right side of the rotor 4 and the body 6 form an oil cavity which is communicated with the circulating oil duct and is an oil supplementing port of the rotor; working medium is pressed into the oil inlet cavity A through the oil storage cavity and enters the working cavity C through the oil return channel E with a large diameter, the working medium is accelerated by the rotor to be heated, then is thrown to the outer edge of the stator, passes through the output hole of the stator, enters the oil outlet cavity B, enters the output oil duct D, enters the heat exchanger for heat exchange, and the cooled medium flows back to the oil return duct E, so that the kinetic energy of the vehicle is circularly converted into heat and is dissipated, and the purpose of controlling the vehicle speed is achieved; 2 sealing rings 7 and 8 are arranged on the excircle of the stator 3 for sealing the end cover 5 and the body 6, and the input cavity and the output cavity of the stator are separated and isolated by a sealing ring 29; compressed air or liquid pressure is introduced from a channel F to the right side of the annular piston 10 to generate meshing thrust; the annular piston can move left and right in the annular piston cylinder body in the body by contacting the end face bearing 11 with the meshing gear, and the annular piston oil seal 9, the annular piston seal ring and the oil seal 12 are sealed to prevent the leakage of retarder media and compressed air or hydraulic oil for pushing the piston; the outer ring of the rear bearing is fixed on the body, and the right side of the outer ring of the rear bearing is isolated from the oil storage cavity of the body by a bearing end cover; a lubricating oil storage cavity formed between the rear bearing and the sealing end cover is communicated with the rear cavity of the rotor through a small oil duct, and is communicated to the middle of the two rear oil seals of the front bearing through an oil duct of a shaft center hole to lubricate an inner sealing lip of the oil seal and lubricate the rear bearing; the outer teeth are uniformly distributed at the outer end of the meshing gear, and splash lubrication is carried out on the ring-shaped piston end face bearing, the right end face bearing of the meshing gear, the rear bearing and other related high-speed rotating parts in no-load. The bearing fastening bolt has a central hole as a lubricating oil passage leading between the left outer oil seal 32 and the inner oil seal 31. Two temperature sensors 27 and 28 are arranged on the outer side of the stator end cover, and the temperatures of inlet and outlet media entering the oil return passage E and the output oil passage D from the working cavity C are respectively monitored.
The annular piston shell is arranged on the retarder body or embedded on the retarder body; the compressed air or hydraulic pressure of the execution ring type piston is controlled by valves such as a 3-position 2-way valve and the like.
The annular actuating piston 10 with compressed air or hydraulic pressure as the power source adopts end face bearings for the moving and possible static contact surfaces, so as to reduce noise and resistance and ensure reliability.
When braking, the right side of the annular piston is communicated with compressed air or hydraulic pressure, the piston moves leftwards, the meshing gear 17 moves leftwards under the pushing of the annular piston 10, the meshing gear is meshed with the rear external teeth of the rotor under the pushing of the execution piston to form a rotor which integrally rotates, and the rotor is stably pushed to the left positioning position; the locking framework moves leftwards simultaneously under the action of the spring force; when the outer conical surface of the synchronous locking ring is contacted with the inner conical surface of the inner hole of the rotor, a reverse friction torque is generated to enable the synchronous locking ring to reversely rotate, the front edges of three inner teeth of the shaft hole are contacted with the front edges of grooves of the shaft hole of the framework, the conical surface of the spline tooth end of the meshing gear is ensured to be opposite to the conical surface of the right tooth end of the synchronous locking ring, and the meshing effect of the locking meshing gear and the synchronous locking ring is achieved, so that under the action of thrust, the friction conical surface of the synchronous locking ring is completely attached to the friction conical surface of the inner hole of the rotor to generate the maximum friction torque to drive the rotor to rotate, when the synchronous locking ring and the rotor and the meshing gear rotate in the same direction by half a tooth, the meshing gear is smoothly meshed with the outer spline of the synchronous locking ring, the spline surface at the right end of the rotor also has the same conical surface, at the moment, because of basic synchronization, the meshing gear is smoothly meshed with the rotor external spline; at the moment, the synchronous locking ring and the external spline of the framework slide to the right in the internal spline of the meshing gear at the same time; under the action of execution pressure, the meshing gear is meshed with the external teeth on the back of the rotor to form an integral rotor which rotates together; then the medium in the oil storage chamber is conveyed to the working chamber C according to the requirement, and the rotor rotates relative to the stator, and the medium is pushed to the stator through the centrifugal action to form resistance, so that corresponding braking force can be generated, and the braking is realized.
During braking, the medium moves at a high speed under the pushing of the rotor, and the speed and the temperature of the medium are reduced and increased under the obstruction of the stator; heat is exchanged with the engine coolant flowing through the other passage of the heat exchanger. The cooled medium flows out of the heat exchanger, passes through the oil return passage E and the oil inlet cavity A and is sucked back to the working cavity C, so that the kinetic energy of the vehicle is changed into the kinetic energy of the medium, and the kinetic energy is converted into heat through the circulation of the medium and the resistance of the stator and is dissipated into the air through exchange.
When the synchronous locking ring is separated, the working medium in the working cavity is removed, the compressed air or hydraulic pressure in the annular piston is withdrawn, and under the action of the separating spring 14 and the locking sliding framework return spring 16, a separating acting force is generated, so that the driving meshing gear moves rightwards, the framework and the synchronous locking ring are driven to move rightwards until the meshing is released, and the synchronous locking ring is separated from the right end face of the rotor.
When the engine is in no-load, the pressure of oil supply of the oil storage cavity is removed, the rotor gradually removes the medium in the working cavity C, the medium enters the oil storage cavity, compressed air or hydraulic pressure of the cavity behind the annular piston is removed, and the meshing gear is gradually pushed rightwards by the separation spring until reaching a right positioning stop point due to the fact that the meshing gear does not have the thrust of the annular piston; the meshing gear, synchronizer and rotor are separated, and the rotor does not rotate together with the shaft, so that no-load loss is reduced to the minimum.
Claims (8)
1. A stator front hydraulic retarder; the method is characterized in that: the retarder comprises a retarder shaft, a front bearing, a stator, a rotor, a stator end cover, a body, a separation spring, an annular piston, a meshing gear, a locking sliding framework, a return spring, a synchronous locking ring, a needle bearing, an outer oil seal, an oil inlet cavity A, an oil outlet cavity B, a working cavity C, an output oil duct D and an oil return duct E; the stator is arranged in front, and the rotor is arranged behind the stator and in a closed cavity in the body; the meshing teeth and the meshing gear of the rotor are connected with the retarder shaft in a torsional mode through a spline and can slide left and right on the shaft spline; the stator and the stator end cover seal a high-pressure oil outlet cavity B and seal a low-pressure oil inlet cavity A by the retarder shaft; a sealing ring is arranged between the rotor and the stator and used for isolating the working cavity C from the oil inlet cavity A; the inner hole of the rotor is provided with a sealing ring to prevent the oil supply cavity of the rotor from being communicated with the oil inlet cavity A of the stator; the space behind the rotor is provided with a separation meshing and executing structure; meshing spline teeth are arranged on the right side of the rotor, and the right ends of the spline teeth are in a conical shape; the meshing gear is arranged behind the rotor, spline teeth of the rotor guide the meshing gear to be smoothly meshed with an external spline of the rotor, and synchronous driving plate torque is generated; the power is smoothly meshed and transmitted by the retarder shaft through the meshing gear and the synchronous locking ring; after the meshing gear is meshed with the rotor, the meshing gear and the rotor rotate together to convey a proper amount of medium in the oil storage cavity to the working cavity C; because the rotor rotates relative to the stator, the medium is pushed to the stator through centrifugal action, and the medium moving at high speed is blocked by the stator, so that corresponding braking force can be generated, and braking is realized; the separating spring seat and the end face bearing are arranged between the separating spring and the rotor to ensure relative movement; the rotor is always positioned at the front end positioning position under the action of the spring, and when the annular piston does not apply force, the meshing gear is separated from the rotor, so that the meshing gear returns to the right side positioning position; the locking sliding framework is matched with a spline of the meshing gear and can slide left and right in the meshing gear, so that the separation of a friction conical surface of the synchronous locking ring from the rotor is ensured, during the separation, working media in a working cavity are removed, compressed air or hydraulic pressure in the annular piston is withdrawn, under the action of a separation spring and a locking sliding framework return spring, separation acting force is generated, the meshing gear moves right, the framework and the synchronous locking ring are driven to move right until the meshing is released, and the synchronous locking ring is separated from the right end surface of the rotor; when the rotor is unloaded, the meshing gear is pushed by the separating spring to move rightwards at the same time until a right positioning dead point, and meanwhile, the meshing gear is separated from the rotor, so that the rotor does not rotate with the shaft any more; during normal driving, the retarder shaft rotates, and the rotor is static.
2. A stator front hydrodynamic retarder according to claim 1; the method is characterized in that: the left side of the meshing gear is limited by a positioning pin; the return spring is positioned between the meshing gear and the sliding framework to ensure that the sliding block and the synchronous ring return to a left dead point when in no-load, and ensure that the synchronous locking ring is positioned at the outer end of the meshing gear teeth when in no-load and a certain gap is ensured; a snap ring is arranged on the left side of the locking sliding framework, and a gap between the synchronous locking ring and a rotor friction conical surface is guaranteed.
3. A stator front hydrodynamic retarder according to claim 1; the method is characterized in that: the rotor and the retarder shaft are supported through a needle bearing; the integral separable rotor is arranged at the rear, the right side of the rotor and the body jointly form an oil cavity, the oil cavity is communicated with the circulating oil duct through an oil hole, the oil cavity is just started to work as an oil supplementing hole, and when air in the cavity is removed, the oil cavity is used as an output port; the stator end cover, the front bearing and the outer oil seal gearbox lubricating oil; the medium flowing out of the heat exchanger enters an oil return passage E of the working cavity C; the oil enters a stator end cover through an oil return passage E and forms a stator oil inlet cavity A with the axis close to the stator, and enters a working cavity C formed by the stator and the rotor through a blade oil port of the stator close to the axis; when braking, the right side of the annular piston is communicated with compressed air or hydraulic pressure, the piston moves leftwards, the meshing gear moves leftwards under the pushing of the annular piston, the meshing gear is meshed with the rear external teeth of the rotor under the pushing of the execution piston to form a rotor which integrally rotates, and the rotor is stably pushed to the left positioning position; the locking framework moves leftwards simultaneously under the action of the spring force; when the outer conical surface of the synchronous locking ring is contacted with the inner conical surface of the inner hole of the rotor, a reverse friction torque is generated, the synchronous locking ring rotates reversely, the end tooth conical surface of the synchronous ring is ensured to be opposite to the end tooth conical surface of the meshing gear to be locked, and when the rotor and the meshing gear are synchronous, the rotor rotates forwards by half tooth by the driving plate torque generated by the end tooth conical surface to realize smooth meshing.
4. A stator front hydrodynamic retarder according to claim 1; the method is characterized in that: when the synchronous locking ring is braked, the meshing gear drives the synchronous ring to move left under the pushing of the annular piston, when the outer friction conical surface of the synchronous ring is just contacted with the inner friction conical surface of the rotor, the synchronous ring rotates reversely by an angle, so that the conical surface of the spline tooth end of the meshing gear is ensured to be opposite to the conical surface of the right tooth end of the synchronous locking ring, and the effect of locking the meshing gear and the synchronous locking ring is achieved, thus under the action of pushing force, the friction conical surface of the synchronous locking ring is completely attached to the friction conical surface of the inner hole of the rotor, the maximum friction torque is generated, and the rotor is driven to rotate; after synchronization, the poking force disc moment is larger than the friction moment, the synchronous locking ring and the rotor and the meshing gear can be poked to rotate forwards for an angle in the same direction until the meshing gear is smoothly meshed with the external spline of the synchronous locking ring, and the right end face of the rotor spline is provided with the same conical surface; at the moment, the synchronous locking ring and the external spline of the framework slide to the right in the internal spline of the meshing gear at the same time; under the action of actuating pressure, the meshing gear is meshed with the external teeth at the back of the rotor to form an integral rotor which rotates together.
5. A stator front hydrodynamic retarder according to claim 1; the method is characterized in that: during braking, working media in the oil storage cavity are pressed into the oil return channel E according to gear requirements and enter the stator oil inlet cavity A through the meshed rotor rotating relative to the stator, then enter the working cavity C, are thrown to the outer end of the stator under the centrifugal action of the rotor, flow into the stator oil outlet cavity B through the stator outer edge output port, enter the heat exchanger through the output oil duct D, flow out of the heat exchanger by the cooled media in heat exchange, flow into the oil inlet cavity A of the stator through the oil return channel E, and then enter the working cavity C of the stator and the rotor.
6. A stator front hydrodynamic retarder according to claim 1; the method is characterized in that: the annular piston shell is arranged on the retarder body or embedded on the retarder body; the compressed air or hydraulic pressure of the execution ring-shaped piston is controlled by valves such as a 3-position 2-way valve and the like; the piston is implemented by a ring type using compressed air or hydraulic pressure as a power source.
7. A stator front hydrodynamic retarder according to claim 1; the method is characterized in that: the device also comprises a synchronous locking ring clamping ring, a rotor needle bearing positioning ring, a rotor positioning ring, an end face bearing, an annular end face bearing, a rear bearing, a meshing gear end face bearing, an input gear and a separating spring seat end face bearing; the retarder shaft is positioned with the front bearing through the space between the platforms; at the front end of a retarder with power input, a stator is axially positioned through a stator end cover; the left side of the meshing gear is limited by a positioning pin; the return spring is positioned between the meshing gear and the sliding framework to ensure that the sliding block and the synchronous ring return to a left dead point when in no-load, and ensure that the synchronous locking ring is positioned at the outer end of the meshing gear teeth when in no-load and a certain gap is ensured; the right side of the meshing gear is positioned on the rear bearing inner sleeve through the end face bearing; a snap ring is arranged on the left side of the locking sliding framework, so that the gap between the synchronous locking ring and the rotor friction conical surface is ensured; the front end of the rotor is axially positioned through the end face bearing and the shaft shoulder and is pushed to a left positioning point under the action of the separation spring all the time; the left side of the end face bearing leans against a shaft shoulder to carry out left side axial positioning, so that the stability of the rotor during rotation and the clearance between the rotor and the stator are ensured; the right side is pressed to the left side positioning position by a spring through an end face bearing spring seat; the rotor and the retarder shaft are supported through a needle bearing; the axial positioning ensures the clearance and the related precision between the stator and the rotor; adjusting a fastening adjusting bolt of the inner ring of the rear bearing, and adjusting and loosening a gap between the front bearing and the rear bearing; the noise of the bearing and the like during movement is reduced, and the gap of the stator and the rotor during braking is ensured, so that the realization of the maximum braking torque is ensured; when the locking sliding framework is in no-load, the locking sliding framework is limited at a left dead point under the action of a return spring; ensuring that the synchronous locking ring is positioned at the outer end of the meshing gear teeth when in no-load and ensuring a certain gap; the meshed gear and the shaft rotate simultaneously, and the skeleton transmits torque and rotates together with the shaft due to the matching of the external spline and the internal tooth of the meshed gear to drive the synchronous locking ring to rotate simultaneously; the left side of the framework shaft sleeve can be positioned through a clamping ring; meanwhile, the synchronous locking ring is limited with the right side of the locking sliding framework groove.
8. A stator front hydrodynamic retarder according to claim 1; the method is characterized in that: the synchronous lock ring leaves at least 1 mm's clearance with rotor internal spline right-hand member, and when the locking slip skeleton was in the leftmost side, the clearance of synchronous lock ring external spline right flank end and meshing gear left side tooth end 1mm at least.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010109626.1A CN111043198A (en) | 2020-02-22 | 2020-02-22 | Stator preposed hydrodynamic retarder |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010109626.1A CN111043198A (en) | 2020-02-22 | 2020-02-22 | Stator preposed hydrodynamic retarder |
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| CN111043198A true CN111043198A (en) | 2020-04-21 |
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| CN114321221A (en) * | 2021-12-31 | 2022-04-12 | 富奥汽车零部件股份有限公司 | Unloading method and unloading device of high-viscosity oil retarder |
| CN114718969A (en) * | 2022-03-31 | 2022-07-08 | 贵阳丽天苍泰科技有限公司 | Hydraulic retarder |
| CN114754091A (en) * | 2022-01-05 | 2022-07-15 | 富奥汽车零部件股份有限公司 | Planet wheel type high-viscosity oil medium high-pressure retarder |
| CN114810870A (en) * | 2022-03-12 | 2022-07-29 | 富奥汽车零部件股份有限公司 | Oil inlet cavity structure of hydraulic retarder |
| CN115163699A (en) * | 2022-06-02 | 2022-10-11 | 阜新德尔汽车部件股份有限公司 | Lubricating structure of hydraulic retarder |
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| CN111963589A (en) * | 2020-08-26 | 2020-11-20 | 一汽解放汽车有限公司 | Structure for reducing no-load loss of hydraulic retarder |
| CN114321222A (en) * | 2021-12-31 | 2022-04-12 | 富奥汽车零部件股份有限公司 | Retarder oil supply method and retarder oil supply system |
| CN114321221A (en) * | 2021-12-31 | 2022-04-12 | 富奥汽车零部件股份有限公司 | Unloading method and unloading device of high-viscosity oil retarder |
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| CN114754091A (en) * | 2022-01-05 | 2022-07-15 | 富奥汽车零部件股份有限公司 | Planet wheel type high-viscosity oil medium high-pressure retarder |
| CN114754091B (en) * | 2022-01-05 | 2023-07-04 | 富奥汽车零部件股份有限公司 | Planetary wheel type high-viscosity oil medium high-pressure retarder |
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| CN114810870B (en) * | 2022-03-12 | 2023-06-30 | 富奥汽车零部件股份有限公司 | Hydraulic retarber advances oil cavity structure |
| CN114718969A (en) * | 2022-03-31 | 2022-07-08 | 贵阳丽天苍泰科技有限公司 | Hydraulic retarder |
| CN115163699A (en) * | 2022-06-02 | 2022-10-11 | 阜新德尔汽车部件股份有限公司 | Lubricating structure of hydraulic retarder |
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