CN106838194B - Free wheel structure of loader torque converter - Google Patents
Free wheel structure of loader torque converter Download PDFInfo
- Publication number
- CN106838194B CN106838194B CN201710214157.8A CN201710214157A CN106838194B CN 106838194 B CN106838194 B CN 106838194B CN 201710214157 A CN201710214157 A CN 201710214157A CN 106838194 B CN106838194 B CN 106838194B
- Authority
- CN
- China
- Prior art keywords
- assembly
- outer ring
- wheel
- guide wheel
- roller
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- 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
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
-
- 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
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/04—Combined pump-turbine units
-
- 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
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
- F16H2041/246—Details relating to one way clutch of the stator
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
The invention discloses a free wheel structure of a loader torque converter, which comprises a shell, a guide wheel seat, a guide wheel assembly, an input assembly and an output assembly, wherein the shell is provided with a guide wheel seat; the input assembly and the output assembly are both arranged in the shell, the guide wheel assembly is sleeved on the guide wheel seat, and the guide wheel seat is fixedly arranged on the shell; the guide wheel assembly comprises a guide wheel fixing sleeve, an outer ring, a needle roller retainer assembly, a plurality of rollers and a star wheel; the inner side of the outer ring is fixedly sleeved in the guide wheel fixing sleeve, the inner side of the star wheel is fixedly sleeved in a stepped hole of the outer ring, a needle roller retainer assembly is arranged between the inner side of the star wheel and a small hole of the stepped hole of the outer ring, a plurality of rollers are arranged between the outer wall of the star wheel and a large hole of the stepped hole of the outer ring, and an inner hole of the star wheel is fixedly sleeved on the guide wheel seat. The guide wheel assembly of the invention is rotatably sleeved on the guide wheel seat, so that the defect that the transmission efficiency is reduced due to the reaction force generated by the turbine to the first-stage turbine and the second-stage turbine when the turbine rotates at high speed is overcome, and the transmission efficiency is high.
Description
Technical Field
The invention relates to the field of mechanical transmission, in particular to a free wheel structure of a loader torque converter.
Background
The hydraulic torque converter is widely applied to hydraulic transmission machinery of automobiles, forklifts, engineering machinery and national defense equipment. The hydraulic torque converter utilizes liquid as a working medium, not only transmits torque, but also increases the torque by multiplying power, so that the engine realizes soft start, and the traction force and the speed of the main machine automatically adapt to the changes of loads and roads. As shown in fig. 1, the conventional torque converter mainly comprises three elements, i.e., a pump impeller 1', a turbine impeller 2' and a guide wheel 3', a flywheel of an engine is connected with the pump impeller through an elastic plate, a loaded gear box is connected with a shaft of the turbine impeller 2', and the guide wheel 3 'is integrally inserted on a guide wheel seat 4'.
When the engine runs, the pump wheel 1 'of the hydraulic torque converter is driven to rotate together with the engine, hydraulic oil in the pump wheel 1' is flushed to the first-stage turbine 21 'and the second-stage turbine 22' from the outer edge of the blade of the pump wheel 1 'under the action of centrifugal force, flows to the guide wheel 3' along the blade of the turbine wheel 2', and then flows through the inner edge of the blade of the guide wheel 3' to form circulating liquid flow. The function of the stator 3 'is to vary the output torque on the turbine 2'. Since the hydraulic oil flowing from the lower edge of the vane of the turbine 2 'to the stator 3' still has a considerable impact force, the impact force can be used to increase the output torque of the turbine 2 'by designing the vanes of the pump 1', the turbine 2 'and the stator 3' to have a certain shape and angle. Before the vehicle starts, the rotating speed of the turbine 2 'is 0, the engine drives the pump wheel 1' to rotate through the elastic plate, and a torque with the magnitude of Mp is generated for hydraulic oil, and the torque is the input torque of the hydraulic torque converter. The hydraulic oil is pushed by the blades of the pump impeller 1' to impact the blades at the upper edge of the turbine 2' at a certain speed, so as to generate impact torque on the turbine 2', and the torque is the output torque of the torque converter. At the moment, the turbine 2' is still, the hydraulic oil rushing towards the turbine 2' flows to the lower edge of the turbine 2' along the blades, rushes towards the guide wheel 3' at a certain speed at the lower edge of the turbine 2' along the same direction as the blades at the outlet of the lower edge of the turbine 2', also generates an impact moment on the guide wheel 3', and flows back to the pump wheel 1' along the blades of the fixed guide wheel 3 '. When the hydraulic oil generates impact torque to the turbine 2 'and the guide wheel 3', the turbine 2 'and the guide wheel 3' also generate reaction torques Mt and Ms with the same magnitude and the opposite direction to the impact torque to the hydraulic oil, wherein the direction of Mt is opposite to the direction of Mp, and the direction of Ms is the same as the direction of Mp. According to the principle of stress balance of hydraulic oil, the following components are obtained: mt = Mp + Ms. Since the torque Mt is equal to and opposite to the impact torque of the hydraulic oil on the turbine 2' (i.e., the output torque of the torque converter) due to the reaction of the turbine 2' to the hydraulic oil, it can be seen that the output torque of the torque converter is equal in value to the sum of the input torque and the reaction torque of the stator 3' to the hydraulic oil. It is clear that this torque is greater than the input torque, i.e. the torque converter has the effect of increasing the torque. The part of the torque converter with increased output torque is the action torque of the stationary stator 3 'on the circularly flowing hydraulic oil, and the value of the action torque depends on the speed of the liquid flow rushing to the stator 3' from the turbine 2 'and the included angle between the direction of the liquid flow and the blade of the stator 3'. When the speed of the liquid flow is unchanged, the larger the included angle between the blade and the liquid flow is, the larger the reaction torque is, and the larger the torque increasing effect of the hydraulic torque converter is. Because the stator 3 'is stationary, when the vehicle starts under the action of the torque output of the torque converter, the turbine 2' connected with the driving wheel also starts to rotate, and the rotating speed of the turbine continuously increases along with the acceleration of the vehicle. At this time, the hydraulic oil rushing towards the turbine 2' from the pump impeller 1' flows along the blades of the turbine 2', and also rotates along with the turbine 2', so that the direction of the hydraulic oil rushing towards the guide wheel 3' from the outlet of the lower edge of the turbine 2' is changed, the direction is not the same as the direction of the blades at the outlet of the turbine 2', but is inclined forwards by an angle along the rotating direction of the turbine 2', the included angle between the flow direction rushing towards the guide wheel 3' and the blades of the guide wheel 3' is reduced, the impact moment applied to the guide wheel 3' is also reduced, and the torque increasing effect of the hydraulic torque converter is also reduced. The higher the vehicle speed is, the higher the rotating speed of the turbine 2' is, the smaller the included angle between the direction of the hydraulic oil rushing towards the guide wheel 3' and the blade of the guide wheel 3' is, and the smaller the torque increasing effect of the hydraulic torque converter is; conversely, the lower the vehicle speed, the greater the torque-up action of the torque converter. Therefore, the torque converter has a larger output torque when the vehicle is running at a low speed than the fluid coupling, and can obtain a larger driving torque for the driving wheels when the vehicle starts, goes uphill, or encounters a larger running resistance. When the rotating speed of the turbine 2 'is increased to a certain value along with the increase of the vehicle speed, the included angle between the direction of hydraulic oil rushing towards the guide wheel 3' and the blade of the guide wheel 3 'is reduced to 0, at the moment, the guide wheel 3' is not impacted by the hydraulic oil, the torque increasing function of the hydraulic torque converter is lost, and the output torque of the hydraulic torque converter is equal to the input torque; if the rotation speed of the turbine 2 'is further increased, the direction of the hydraulic oil rushing towards the guide wheel 3' is continuously inclined forwards, so that the hydraulic oil rushes against the back surface of the blade of the guide wheel 3', and at the moment, the direction of the reaction torque Ms of the guide wheel 3' to the hydraulic oil is opposite to the direction of the torque Mp of the pump wheel 1 'to the hydraulic oil, so that the output torque on the turbine 2' is the difference between the two, namely Mt = Mp-Ms, the output torque of the hydraulic torque converter is smaller than the input torque, and the transmission efficiency is reduced accordingly. Therefore, by adopting the hydraulic torque converter fixed by the guide wheel 3', when the rotating speed of the turbine 2' is lower, the transmission efficiency of the hydraulic torque converter is higher than that of the hydraulic coupler; when the rotational speed of the turbine 2' increases to a certain value, the transmission efficiency of the torque converter is equal to that of the fluid coupling; when the rotating speed of the turbine 2' continues to increase, the transmission efficiency of the hydraulic torque converter is smaller than that of the hydraulic coupler, and the output torque of the hydraulic torque converter is reduced; in order to overcome the problem that when the turbine 2' rotates at a high speed, the transmission efficiency is reduced due to the reaction force generated by the first-stage turbine 21' and the second-stage turbine 22', the present invention is developed.
Disclosure of Invention
The invention aims to provide a free wheel structure of a loader torque converter with high transmission efficiency.
In order to achieve the purpose, the technical solution of the invention is as follows:
the invention relates to a free wheel structure of a loader torque converter, which comprises a shell, a guide wheel seat, a guide wheel assembly, an input assembly and an output assembly; the input assembly and the output assembly are both arranged in the shell, the guide wheel assembly is sleeved on the guide wheel seat and is positioned between the input assembly and the output assembly, and the guide wheel seat is fixedly arranged on the shell; the guide wheel assembly comprises a guide wheel fixing sleeve, an outer ring, a one-way clutch rolling assembly and a star wheel; the guide wheel fixing sleeve is provided with blades; the outer ring is in a step shape, the inner part of the outer ring is hollow, and the outer wall of the small-diameter end is in interference fit with the guide wheel fixing sleeve; the inner hole of the star wheel is fixedly sleeved on the guide wheel seat, and the outer wall of the star wheel is movably sleeved in the stepped hole of the outer ring; the one-way clutch rolling assembly is arranged between the outer ring and the star wheel and ensures that the outer ring can only rotate clockwise or anticlockwise in a one-way mode.
Further, the one-way clutch rolling assembly comprises a needle roller retainer assembly and a plurality of rollers; the needle roller retainer assembly is arranged between the outer wall of the star wheel and the small hole of the outer ring stepped hole, a plurality of concave curved surface grooves are formed in the outer wall of the star wheel relative to the large hole of the outer ring stepped hole, each concave curved surface groove is composed of two sections of first curved surfaces and second curved surfaces with different curvatures, each first curved surface is a logarithmic spiral line, and each second curved surface is an arc; a roller space for containing the rollers is formed between the concave curved surface groove on the outer wall of the star wheel and the large hole of the outer ring stepped hole, and the rollers are movably sleeved in the roller space respectively.
Furthermore, the center distance between two adjacent rollers is L, the radius of the rollers is R, the shortest distance of the outer contour lines of the two rollers is M, M = L-2R, and the distance of M is 0-0.2.
Furthermore, the wedge angle formed by the first curved surface of the outer wall of the star wheel and the inner wall of the large hole of the outer ring stepped hole of the roller is 8-10 degrees, and the roller is meshed with the first curved surface of the outer wall of the star wheel and the inner wall of the large hole of the outer ring stepped hole at the moment.
The present invention also provides another embodiment of a one-way clutching rolling assembly that includes a needle cage assembly, a plurality of rollers, a plurality of roller springs, a plurality of spring pins; the roller pin retainer assembly is arranged between the outer wall of the star wheel and the small hole of the outer ring stepped hole, a plurality of toothed surfaces are arranged on the outer wall of the star wheel relative to the large hole of the outer ring stepped hole, the plurality of rollers are movably abutted to the plurality of toothed surfaces respectively, a roller spring and a spring ejector pin are sequentially and movably sleeved in each toothed surface, and the outer end of the spring ejector pin is abutted to the roller.
Furthermore, the wedge angle of the roller between the outer wall of the star wheel and the inner wall of the large hole of the outer ring stepped hole is 6-8 degrees, and the roller is meshed with the outer wall of the star wheel and the inner wall of the large hole of the outer ring stepped hole.
Further, the two embodiments also comprise a baffle plate, a circlip for a hole and a circlip for a shaft; the baffle is sleeved on the star wheel and positioned between the outer ring and the star wheel, the inner side of the baffle abuts against the outer end of the roller in the one-way clutch rolling assembly, the hole is clamped in the clamping groove of the outer ring by the elastic check ring and abuts against the outer side of the baffle, and the shaft is fixedly sleeved on the star wheel by the elastic check ring and abuts against the roller pin retainer assembly in the one-way clutch rolling assembly.
Further, a notch is formed in the outer side of the star wheel, and an oil channel in the guide wheel seat extends inwards to the notch, so that oil can flow into the pump wheel of the input assembly from the notch.
Furthermore, the input assembly consists of an elastic plate, a cover wheel, a pump wheel and a transfer gear, wherein the elastic plate is connected with a flywheel of the diesel engine through a stud, the elastic plate is connected with the cover wheel through a bolt, the cover wheel is connected with the front end of the pump wheel through a bolt, the rear end of the pump wheel is connected with the transfer gear through a bolt, and the pump wheel is rotatably sleeved on the guide wheel seat through two first bearings; the output assembly comprises a first-stage turbine assembly and a second-stage turbine, the first-stage turbine assembly is rotatably connected with the cover wheel through a second bearing, and the second-stage turbine is rotatably arranged on a first-stage turbine shell in the first-stage turbine assembly through a third bearing.
Furthermore, the first-stage turbine assembly comprises a first-stage turbine, a first-stage turbine cover and a first-stage turbine shell, wherein the first-stage turbine is connected with the first-stage turbine cover through an elastic pin, and the first-stage turbine cover is riveted on the first-stage turbine shell through a rivet.
After the scheme is adopted, the guide wheel assembly comprises the guide wheel fixing sleeve, the outer ring, the needle roller retainer assembly, the plurality of rollers and the star wheel which are rotatably sleeved on the guide wheel seat, so that the defect that the transmission efficiency is reduced due to the reaction force of hydraulic oil flowing through the guide wheel assembly on the first-stage turbine and the second-stage turbine when the turbines rotate at high speed is overcome, and the transmission efficiency is high.
The invention is further described with reference to the following figures and specific examples.
Drawings
FIG. 1 is a cross-sectional view of a conventional loader torque converter;
FIG. 2 is a cross-sectional view of the present invention;
FIG. 3 is a cross-sectional view of a first embodiment of the idler assembly of the present invention;
FIG. 4 is an exploded perspective view of a first embodiment of the idler assembly of the present invention;
FIG. 5 is an elevation view of a first embodiment of the idler assembly of the present invention;
FIG. 6A is an elevation view of a first embodiment of a spider assembly of the present invention;
FIG. 6B is a cross-sectional view of a spider of the first embodiment of the idler assembly of the present invention;
FIG. 6C is a cross-sectional view of the outer ring of the first embodiment of the idler assembly of the present invention;
FIG. 7-1 is a schematic view showing a roller fitting state of the first embodiment of the guide wheel assembly of the present invention;
fig. 7-2 is a schematic view showing a roller disengaging state of the first embodiment of the guide wheel assembly of the present invention;
FIG. 8 is an exploded perspective view of a second embodiment of the idler assembly of the present invention;
FIG. 9 is an elevation view of a second embodiment of the idler assembly of the present invention;
FIG. 10-1 is a schematic diagram of a roller engagement condition of a second embodiment of the idler assembly of the present invention;
FIG. 10-2 is a schematic diagram of a roller disengagement condition of a second embodiment of the idler assembly of the present invention;
fig. 10-3 is a partial enlarged view of fig. 10-2.
Detailed Description
As shown in fig. 2, the present invention is a freewheel structure of a torque converter of a loader, comprising a housing 1, a guide wheel seat 2, a guide wheel assembly 3, an input assembly 4, and an output assembly 5.
The input assembly 4 and the output assembly 5 are both installed in the shell 1, the guide wheel assembly 3 is sleeved on the guide wheel seat 2 and is located between the input assembly 4 and the output assembly 5, and the guide wheel seat 2 is fixedly installed on the shell 1.
The input assembly 4 consists of an elastic plate 41, a cover wheel 42, a pump wheel 43 and a transfer gear 44. The elastic plate 41 is connected with a flywheel of the diesel engine through a stud bolt, the elastic plate 41 is connected with the cover wheel 42 through a bolt, the cover wheel 42 is connected with the front end of the pump wheel 43 through a bolt, the rear end of the pump wheel 43 is connected with the transfer gear 44 through a bolt, the pump wheel 43 is rotatably sleeved on the guide wheel seat 2 through two first bearings 45, and the transfer gear 44 provides power for a speed change pump, a working pump and a steering pump.
The output component 5 consists of a first-stage turbine assembly 51 and a second-stage turbine 52. The first-stage turbine assembly 51 consists of a first-stage turbine 511, a first-stage turbine cover 512 and a first-stage turbine shell 513; the first turbine 511 is coupled to a first turbine shroud 512 by a spring pin 514, and the first turbine shroud 512 is riveted to a first turbine shell 513 by rivets. The first-stage turbine assembly 51 is rotatably connected with the cover wheel 42 through a second bearing 54, the second-stage turbine 52 is rotatably mounted on a first-stage turbine shell 513 in the first-stage turbine assembly 51 through a third bearing 55, and the first-stage turbine 51 and the second-stage turbine 52 supply power to a first-stage input gear of the gearbox through internal splines.
As shown in fig. 3-7, a first embodiment of the guide wheel assembly 3 is shown, the guide wheel assembly 3 is a roller-type structure, and the guide wheel assembly 3 includes a guide wheel fixing sleeve 31, an outer ring 32, a one-way clutch rolling assembly 33, a shaft circlip 34, a star wheel 35, a baffle 36, and a hole circlip 37. The inner ring circumference of the guide wheel fixing sleeve 31 is provided with a ring-shaped distribution of blades 311, and the blades 311 are arranged along the same inclined direction; the outer ring 32 is a stepped cylinder, the inner part of the outer ring is hollow, and the outer wall of the small-diameter end 321 and the guide wheel fixing sleeve 31 are mutually nested to form interference fit; the inner hole of the star wheel 35 is fixedly sleeved on the guide wheel seat 2, the outer wall of the star wheel is provided with a plurality of concave curved surface grooves 352, the concave curved surface grooves 352 are opposite to the large-diameter end 322 of the outer ring 32, the concave curved surface grooves 352 are formed by a first curved surface 3521 and a second curved surface 3522 which have different curvatures, wherein the first curved surface 3521 is a logarithmic spiral line, and the second curved surface 3522 is an arc; and the star wheel 35 is nested in the stepped hole of the outer ring 32, and one side of the concave curved groove 352 is abutted against the stepped surface 323 of the stepped hole. The one-way clutch rolling assembly 33 comprises a needle roller cage assembly 331 and a plurality of rollers 332. The needle roller retainer assembly 331 is arranged between the outer side of the star wheel 35 and the small hole of the stepped hole 321 of the outer ring 32, the rollers 332 are arranged in a roller space formed between the concave curved groove 352 on the outer wall of the star wheel 35 and the large-diameter end 322 of the outer ring 32 (the large hole position of the outer ring stepped hole), the plurality of rollers 332 are respectively movably sleeved in the roller space, the center distance between two adjacent rollers 332 is L, the radius of the roller 332 is R, the shortest distance between the contour lines of the two rollers 332 is M, M = L-2R, and the distance of M is 0-0.2, so that when the outer ring 32 drives at least one roller 332 to move towards the first curved surface 3521, the adjacent rollers 332 are abutted against each other to bear force, and each roller 332 is ensured to move towards the first curved surface 3521; conversely, when the outer ring 32 drives at least one roller 332 to move toward the second curved surface 3522, the adjacent rollers 332 are also pressed against each other, so as to disengage from each other more quickly.
The baffle plate 36 is sleeved on the star wheel 35 and positioned between the outer ring 32 and the star wheel 35, the inner side of the baffle plate 36 abuts against the outer end of the roller 34, the hole circlip 37 is clamped in the clamping groove of the outer ring 32 and abuts against the outer side of the baffle plate 36, the shaft circlip 38 is fixedly sleeved on the star wheel 35 and abuts against the needle roller retainer assembly 33, and due to the arrangement of the needle roller retainer assembly 331, when the roller 332 is prevented from being separated from the inner wall of the outer ring 32, the coaxiality between the outer ring 32 and the star wheel 35 is ensured through the needle roller retainer assembly 33, so that the outer ring 32 can keep the fixed central axis to rotate in a non-wedged state without generating deflection.
In order to mount the rollers 34 between the outer ring 32 and the star wheel 35, the outer ring 32 needs to be formed into a stepped cylindrical shape, which cannot be directly formed into a cylindrical shape, because the outer ring 32 and the guide wheel fixing sleeve 31 are tightly fitted to each other, and the rollers 34 are mounted on the outer ring 32 below the guide wheel fixing sleeve 31 without a space, so that the outer ring 32 needs to be formed into a stepped shape, and the position of the large-diameter end 322 is used for mounting the rollers, so that the first bearing 45 is shifted to the right, and in order to make the oil in the oil passage 21 in the guide wheel base 2 smoothly flow into the input unit 4, a notch 351 needs to be provided outside the star wheel 35, and the oil passage 21 in the guide wheel base 2 is extended to the direction of the guide wheel assembly 3 to the notch 351.
The working principle of the guide wheel assembly 3 of the invention is as follows:
as shown in fig. 7-1 and 7-2, the guide wheel assembly 3 of the present embodiment operates on the following principle: when the vehicle is started, the flywheel of the engine drives the pump impeller 43 to rotate, hydraulic oil flows into the first-stage turbine assembly 51 and the second-stage turbine 52 in the output assembly 5 in sequence at a certain speed under the pushing of the blades of the pump impeller 43, the first-stage turbine assembly 51 and the second-stage turbine 52 are driven to rotate, and the hydraulic oil flows out of the second-stage turbine 52 and flows back to the pump impeller 43 through the guide wheel assembly; in an initial state, the rotation speed of the pump impeller 43 is higher than the rotation speeds of the first-stage turbine 511 and the second-stage turbine 52, the total torque/the pump impeller torque of the first-stage turbine 511 and the second-stage turbine 52 is greater than 1, the impact direction of hydraulic oil flowing into the guide wheel assembly 3 is opposite to the inclination direction of the blades 311 of the outer ring fixing sleeve 31, so that the outer ring 32 is driven to drive the roller 332 to rotate towards the first curved surface 3521 on the outer wall of the star wheel 35, a first tangent line is formed between the roller 332 and the first curved surface 3521 on the outer wall of the star wheel 35, a second tangent line is formed between the roller 332 and the inner wall of the large stepped hole of the outer ring 32, a wedge angle α formed between the first tangent line and the second tangent line is 8-10 °, so that the roller 33 fits into a space between the first curved surface 3521 on the outer wall of the star wheel 35 and the inner wall of the large stepped hole of the outer ring 32, at this time, the outer ring 32, the roller 332 and the star wheel 35 are rigidly connected, and the outer ring 32 cannot rotate freely; with the increasing of the rotation speed of the turbine, when the turbine torque/the pump wheel torque exceeds the total torque/the pump wheel torque =1 of the first-stage turbine 511 and the second-stage turbine 52 at the coupling point, the impact direction of the hydraulic oil flowing into the guide wheel assembly 3 is the same as the inclination direction of the blades 311 of the guide wheel fixing sleeve 31, the outer ring 32 drives the rollers 332 to separate from the first curved surface 3521 on the outer wall of the star wheel 35, the outer ring 32 can move around the star wheel 35 towards the second curved surface 3522 under the driving of the guide wheel fixing sleeve 31, because the roller 332 is located on the second curved surface 3522 on the outer wall of the star wheel 35 and forms a wedge angle γ > 18 ° with the inner wall of the large hole of the stepped hole of the outer ring 32 (see fig. 7-2), the rollers cannot self-lock with the star wheel 35 and the outer ring 32, the rollers 332 can freely rotate in the accommodating space formed by the second curved surface 3522 on the outer wall of the star wheel 35 and the inner wall of the large hole of the stepped hole of the outer ring 32, the guide wheel fixing sleeve 31 can freely rotate around the star wheel 35 in one direction under the driving of the hydraulic oil, and the defect that the reduction of the transmission efficiency of the hydraulic oil generated by the reaction force generated by the hydraulic oil generated by the first-stage turbine 3 when the turbine rotates at a high speed is greatly reduced when the turbine.
As shown in fig. 8 and 9, a second embodiment of the guide wheel assembly 3 is shown, and the guide wheel assembly 3A is of a pin-ejecting type structure, which is basically the same as that of the first embodiment shown in fig. 4, and includes an outer ring 32A, a shaft circlip 33A, a one-way clutch rolling assembly, a star wheel 35A, a retainer plate 36A, and a hole circlip 37A, except that the one-way clutch rolling assembly includes a needle roller holder assembly 341A, a plurality of rollers 342A, a plurality of roller springs 343A, and a plurality of spring pins 344A; the needle roller retainer assembly 341A is arranged between the inner side of the star wheel 35A and the small hole of the outer ring stepped hole, the outer wall of the outer side of the star wheel 35A is provided with a plurality of toothed surfaces 350A, the plurality of rollers 342A are respectively movably abutted against the plurality of toothed surfaces 350A, a roller spring 343A and a spring ejector pin 344A are sequentially movably sleeved in each toothed surface 350A, and the outer end of the spring ejector pin 344A is abutted against the roller 342A.
The working principle of the embodiment is basically consistent with that of the first embodiment, except that at the moment when the turbine torque/pump wheel torque is larger than 1, the technical scheme for enabling the outer ring 32A of the guide wheel assembly 3 to be meshed with the star wheel 35A is that the roller 342A, the roller spring 343A, the spring ejector pin 344A, the tooth-shaped surface 350A and the inner wall of the outer ring 32A are matched with each other, namely when the impact direction of hydraulic oil flowing into the guide wheel assembly 3 is opposite to the inclined direction driven by the blade 381A of the guide wheel fixing sleeve 38A, the hydraulic oil outer ring 32A drives the roller 342A to move towards the tooth-shaped surface 350A of the star wheel 35A, and as the wedge angle beta between the outer wall of the star wheel 35A and the inner wall of the large hole of the stepped hole of the outer ring 32A is 6-8 degrees, at the moment, the outer ring 32A is meshed with the star wheel 35A through the roller 342A, the outer ring 32A is rigidly connected with the star wheel 35A, and the guide wheel fixing sleeve 38A cannot rotate freely; with the increasing of the turbine rotation speed, when the turbine torque/the pump torque =1, the impact direction of the hydraulic oil flowing into the guide wheel assembly 3 is the same as the inclination direction of the blade 381A of the guide wheel fixing sleeve 38A, and the outer ring 32A drives the roller 342A to overcome the elastic restoring force of the spring top pin 344A, so that the outer ring 32A and the star wheel 35A are separated from each other, and a gap (see fig. 10-3) is generated between the roller 342A and the star wheel 35A, and the outer ring 32A can freely rotate around the star wheel 35A in one direction under the driving of the guide wheel fixing sleeve 38A, thereby greatly reducing the defect that the transmission efficiency is reduced due to the reactive force of the hydraulic oil flowing through the guide wheel assembly 3 on the first-stage turbine and the second-stage turbine when the turbine rotates at a high speed.
The above description is only a preferred embodiment of the present invention, and therefore should not be taken as limiting the scope of the invention, and all equivalent variations and modifications made within the claims and the specification of the present invention should be included in the scope of the present invention.
Claims (10)
1. A free wheel structure of a torque converter of a loader comprises a shell, a guide wheel seat, a guide wheel assembly, an input assembly and an output assembly; the input assembly and the output assembly are both arranged in the shell, the guide wheel assembly is sleeved on the guide wheel seat and is positioned between the input assembly and the output assembly, and the guide wheel seat is fixedly arranged on the shell; the method is characterized in that: the guide wheel assembly comprises a guide wheel fixing sleeve, an outer ring, a one-way clutch rolling assembly and a star wheel; the guide wheel fixing sleeve is provided with blades; the outer ring is in a step shape, the inner part of the outer ring is hollow, and the outer wall of the small-diameter end of the outer ring is in interference fit with the guide wheel fixing sleeve; the inner hole of the star wheel is fixedly sleeved on the guide wheel seat, and the outer wall of the star wheel is movably sleeved in the stepped hole of the outer ring; the one-way clutch rolling assembly is arranged between the outer ring and the star wheel and ensures that the outer ring can only rotate clockwise or anticlockwise in a one-way mode.
2. The freewheel structure of loader torque converter according to claim 1 characterized in that: the one-way clutch rolling assembly comprises a needle roller retainer assembly and a plurality of rollers; the roller pin retainer assembly is arranged between the outer wall of the star wheel and the small hole of the outer ring stepped hole, a plurality of concave curved surface grooves are formed in the outer wall of the star wheel relative to the large hole of the outer ring stepped hole, each concave curved surface groove is formed by two sections of first curved surfaces and second curved surfaces, the curvatures of the first curved surfaces are different, the first curved surfaces are logarithmic spirals, and the second curved surfaces are circular arcs; the concave curved surface groove on the outer wall of the star wheel and the large hole of the outer ring stepped hole form a roller space for containing the rollers, and the plurality of rollers are respectively movably sleeved in the roller space.
3. The freewheel structure of loader torque converter according to claim 2 characterized in that: the center distance between two adjacent rollers in the plurality of rollers is L, the radius of the rollers is R, the shortest distance between the outer contour lines of the two rollers is M, M = L-2R, and the distance of M is 0-0.2.
4. The freewheel structure of loader torque converter according to claim 2 characterized in that: the wedge angle formed by the first curved surface of the outer wall of the star wheel and the inner wall of the large hole of the outer ring stepped hole is 8-10 degrees, and the roller is meshed with the first curved surface of the outer wall of the star wheel and the inner wall of the large hole of the outer ring stepped hole.
5. The freewheel structure of loader torque converter according to claim 1 characterized in that: the one-way clutch rolling assembly comprises a needle roller retainer assembly, a plurality of rollers, a plurality of roller springs and a plurality of spring ejector pins; the needle roller retainer assembly is arranged between the outer wall of the star wheel and the small hole of the outer ring stepped hole, a plurality of toothed surfaces are arranged on the outer wall of the star wheel relative to the large hole of the outer ring stepped hole, a plurality of roller are respectively movably abutted against the plurality of toothed surfaces, a roller spring and a spring ejector pin are sequentially movably sleeved in each toothed surface, and the outer end of the spring ejector pin is abutted against the roller.
6. The freewheel structure of loader torque converter according to claim 5 characterized in that: the wedge angle of the roller between the outer wall of the star wheel and the inner wall of the large hole of the outer ring stepped hole is 6-8 degrees, and the roller is meshed with the outer wall of the star wheel and the inner wall of the large hole of the outer ring stepped hole.
7. The freewheel structure of a loader torque converter according to claim 2 or 5 characterized in that: the device also comprises a baffle plate, an elastic retainer ring for the hole and an elastic retainer ring for the shaft; the baffle is sleeved on the star wheel and positioned between the outer ring and the star wheel, the inner side of the baffle abuts against the outer end of the roller in the one-way clutch rolling assembly, the hole is clamped in the clamping groove of the outer ring by the elastic check ring and abuts against the outer side of the baffle, and the shaft is fixedly sleeved on the star wheel by the elastic check ring and abuts against the roller pin retainer assembly in the one-way clutch rolling assembly.
8. The freewheel structure of loader torque converter according to claim 1 characterized in that: the star wheel outside be equipped with the breach, the oil duct in the guide wheel seat inwards extend to this breach department to oil can flow into the pump impeller of input assembly from the breach.
9. The freewheel structure of a loader torque converter according to claim 1 characterized in that: the input assembly consists of an elastic plate, a cover wheel, a pump wheel and a transfer gear, wherein the elastic plate is connected with a flywheel of the diesel engine through a stud, the elastic plate is connected with the cover wheel through a bolt, the cover wheel is connected with the front end of the pump wheel through a bolt, the rear end of the pump wheel is connected with the transfer gear through a bolt, and the pump wheel is rotatably sleeved on a guide wheel seat through two first bearings; the output assembly comprises a first-stage turbine assembly and a second-stage turbine, the first-stage turbine assembly is rotatably connected with the cover wheel through a second bearing, and the second-stage turbine is rotatably arranged on a first-stage turbine shell in the first-stage turbine assembly through a third bearing.
10. The freewheel structure of a loader torque converter according to claim 9 characterized in that: the first-stage turbine assembly is composed of a first-stage turbine, a first-stage turbine cover and a first-stage turbine shell, the first-stage turbine is connected with the first-stage turbine cover through an elastic pin, and the first-stage turbine cover is riveted on the first-stage turbine shell through rivets.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710214157.8A CN106838194B (en) | 2017-04-01 | 2017-04-01 | Free wheel structure of loader torque converter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710214157.8A CN106838194B (en) | 2017-04-01 | 2017-04-01 | Free wheel structure of loader torque converter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106838194A CN106838194A (en) | 2017-06-13 |
| CN106838194B true CN106838194B (en) | 2023-04-14 |
Family
ID=59142813
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710214157.8A Active CN106838194B (en) | 2017-04-01 | 2017-04-01 | Free wheel structure of loader torque converter |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106838194B (en) |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09112650A (en) * | 1995-10-20 | 1997-05-02 | Exedy Corp | Torque converter |
| JPH109364A (en) * | 1996-06-25 | 1998-01-13 | Exedy Corp | Supporting structure for stator of torque converter |
| CN101338800A (en) * | 2008-07-14 | 2009-01-07 | 江苏泰隆减速机股份有限公司 | Roller type brake |
| CN203023422U (en) * | 2012-12-27 | 2013-06-26 | 山推工程机械股份有限公司 | Hydraulic torque converter |
| CN203442010U (en) * | 2013-08-22 | 2014-02-19 | 法雷奥汽车自动传动系统(南京)有限公司 | One-way clutch used for automobile hydraulic torque converter |
| CN204041778U (en) * | 2014-08-08 | 2014-12-24 | 洛阳雷斯达传动有限公司 | A kind of free wheel device for high-power special vehicle torque-converters |
| CN104500678A (en) * | 2014-12-22 | 2015-04-08 | 贵州凯星液力传动机械有限公司 | Transmission structure of hydraulic torque converter |
| CN104976248A (en) * | 2015-06-26 | 2015-10-14 | 传孚科技（厦门）有限公司 | Bidirectional overrunning clutch |
| CN205446461U (en) * | 2015-12-22 | 2016-08-10 | 徐州徐工传动科技有限公司 | Double roller one way clutch structure |
| CN206723390U (en) * | 2017-04-01 | 2017-12-08 | 厦门厦工机械股份有限公司 | The free wheel construction of loading machine torque-converters |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6997295B2 (en) * | 2002-07-03 | 2006-02-14 | Pederson Jack E | Clutch having elements capable of independent operation |
-
2017
- 2017-04-01 CN CN201710214157.8A patent/CN106838194B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09112650A (en) * | 1995-10-20 | 1997-05-02 | Exedy Corp | Torque converter |
| JPH109364A (en) * | 1996-06-25 | 1998-01-13 | Exedy Corp | Supporting structure for stator of torque converter |
| CN101338800A (en) * | 2008-07-14 | 2009-01-07 | 江苏泰隆减速机股份有限公司 | Roller type brake |
| CN203023422U (en) * | 2012-12-27 | 2013-06-26 | 山推工程机械股份有限公司 | Hydraulic torque converter |
| CN203442010U (en) * | 2013-08-22 | 2014-02-19 | 法雷奥汽车自动传动系统(南京)有限公司 | One-way clutch used for automobile hydraulic torque converter |
| CN204041778U (en) * | 2014-08-08 | 2014-12-24 | 洛阳雷斯达传动有限公司 | A kind of free wheel device for high-power special vehicle torque-converters |
| CN104500678A (en) * | 2014-12-22 | 2015-04-08 | 贵州凯星液力传动机械有限公司 | Transmission structure of hydraulic torque converter |
| CN104976248A (en) * | 2015-06-26 | 2015-10-14 | 传孚科技（厦门）有限公司 | Bidirectional overrunning clutch |
| CN205446461U (en) * | 2015-12-22 | 2016-08-10 | 徐州徐工传动科技有限公司 | Double roller one way clutch structure |
| CN206723390U (en) * | 2017-04-01 | 2017-12-08 | 厦门厦工机械股份有限公司 | The free wheel construction of loading machine torque-converters |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106838194A (en) | 2017-06-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP4935006B2 (en) | Fluid transmission device | |
| JP6338003B1 (en) | Electric car | |
| US9068638B2 (en) | Vehicle drive device | |
| US20130149110A1 (en) | Off axis pump with integrated chain and sprocket assembly | |
| WO2011062265A1 (en) | Drive device for vehicle | |
| CN100575746C (en) | The stator supporting apparatus that is used for torque-converters | |
| MXPA02004254A (en) | Overrunning coupling assembly | |
| JP6072925B2 (en) | Stator shaft fixing structure of transmission | |
| JP3293463B2 (en) | One-way clutch mechanism for torque converter | |
| CN102606706B (en) | Starting device having a throttle plate | |
| US5918461A (en) | Stator assembly having single direction anti-rotation device | |
| CN106838194B (en) | Free wheel structure of loader torque converter | |
| US9303746B2 (en) | Vehicular torque converter | |
| US7350352B2 (en) | Fluid coupling | |
| US10808819B2 (en) | Torque converter assembly and single face torque converter clutch | |
| US7048502B2 (en) | Fluid coupling | |
| JP6415522B2 (en) | Torque converter stator structure | |
| US20130256074A1 (en) | Turbine assembly having improved torque capacity | |
| US10274081B2 (en) | Stator assembly of hydraukinetic torque converter with pivotable stator blades, and method for making the same | |
| CN109863332B (en) | Torque converter with one-way clutch for automatic transmission | |
| JP2017114436A (en) | Vehicular driving device | |
| JP2012096677A (en) | Drive device for vehicle | |
| JP5081472B2 (en) | Oil passage structure of starter | |
| JP4375179B2 (en) | Housing member and fluid transmission device unit | |
| JP3026953B2 (en) | Torque converter |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| CB03 | Change of inventor or designer information | ||
| CB03 | Change of inventor or designer information |
Inventor after: Qiu Haibin Inventor after: Lin Xianzong Inventor after: Weng Jiaxiang Inventor after: Ye Chaoqun Inventor after: Wu Jinshui Inventor after: Pan Zuobin Inventor after: Zhang Rong Inventor after: Zhao Shaonan Inventor after: Yue Chenglin Inventor before: Qiu Haibin Inventor before: Pan Zuobin Inventor before: Zhang Rong Inventor before: Zhao Shaonan Inventor before: Weng Jiaxiang Inventor before: Yue Chenglin |
|
| TA01 | Transfer of patent application right | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20171121 Address after: Xiamen City, Fujian province 361000 Wo Road, Siming District of Xiamen No. 668 Applicant after: XIAMEN XGMA MACHINERY Co.,Ltd. Applicant after: ZHEJIANG LINHAI MACHINERY Co.,Ltd. Address before: Xiamen City, Fujian province 361008 Wo Road, Siming District of Xiamen No. 668 Applicant before: XIAMEN XGMA MACHINERY Co.,Ltd. |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant |