CN114215890A - Face gear multi-gear speed change device - Google Patents
Face gear multi-gear speed change device Download PDFInfo
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- CN114215890A CN114215890A CN202111541229.2A CN202111541229A CN114215890A CN 114215890 A CN114215890 A CN 114215890A CN 202111541229 A CN202111541229 A CN 202111541229A CN 114215890 A CN114215890 A CN 114215890A
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/42—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion with gears having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
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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
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/025—Synchro rings
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/42—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion with gears having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
- F16H3/426—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion with gears having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable the teeth being arranged on a generally flat, e.g. disc-type surface
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Abstract
The invention discloses a face gear multi-gear speed change device, which comprises an input shaft, a clutch, a transmission shaft, a cylindrical gear set, a plurality of synchronous rings, a plurality of shifting forks, a face gear set and an output shaft, wherein the input shaft is connected with the clutch; the power is transmitted to the transmission shaft from the input shaft through the clutch, the transmission shaft drives the synchronizing ring to rotate, the synchronizing ring drives the cylindrical gear to rotate through the clamping structure, the cylindrical gear drives the meshed face gear to rotate, and finally the output shaft outputs the power; during gear shifting, the clutch is separated, the power source is disconnected, and the shifting fork is shifted to enable the synchronizing ring to be clamped with the other cylindrical gear; after gear shifting is completed, the clutch is closed, the power source is connected, power is output to the output shaft again, and the output rotating speed and the output torque synchronously change due to the fact that the gear ratio of the cylindrical gear and the face gear changes. The device has small structure size and light weight. Compared with the traditional cylindrical gear transmission, the face gear set can greatly reduce the occupied space of the gear, and the size and the weight are greatly reduced.
Description
Technical Field
The invention belongs to the technical field of mechanical engineering, and particularly relates to a multi-gear speed changing device.
Background
Mechanical transmission is one of the core technologies of mechanical engineering disciplines, and a mechanical transmission system is widely applied in the industrial field. With the development of industrial technology, various mechanical devices have higher and higher requirements on speed changing devices, such as watches, engineering machines and the like, and the speed changing devices have high reliability, small size and simple structures.
At present, a speed change device generally uses a speed change principle taking a cylindrical gear transmission technology as a core, and power passes through cylindrical gears meshed with different gear ratios to realize change of rotating speed and torque. The speed change principle can be used for realizing speed change of different gears so as to adapt to different use environments. For example, in an automobile gearbox, multiple groups of cylindrical gear pairs are used for realizing the speed change of multiple gears, different gears correspond to different use environments, for example, a low gear is used in occasions requiring large torque such as starting and climbing, and a high gear is used in occasions requiring high rotating speed such as high speed. However, the multi-gear speed changing device needs a plurality of cylindrical gears, and has the disadvantages of complex structure, high design and manufacturing difficulty, difficult maintenance and high processing cost.
Face gear transmission technology is a transmission form which has been developed in recent years, and unlike other transmission forms, a gear which is meshed with a face gear is a standard involute cylindrical gear. The transmission mode has the advantages of large transmission ratio, simple structure, large transmission load, large contact ratio, insensitivity to axial installation error of the cylindrical gear and the like. The face gear transmission technology is mainly used for electric tools, toys and middle-sized machines such as helicopters in recent years. However, the existing face gear transmission technology is only used in a single-stage transmission system, and a multi-gear speed change device adopting a plurality of groups of face gear pair transmission is not seen.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention provides a face gear multi-gear speed change device which comprises an input shaft, a clutch, a transmission shaft, a cylindrical gear set, a plurality of synchronous rings, a plurality of shifting forks, a face gear set and an output shaft; the power is transmitted to the transmission shaft from the input shaft through the clutch, the transmission shaft drives the synchronizing ring to rotate, the synchronizing ring drives the cylindrical gear to rotate through the clamping structure, the cylindrical gear drives the meshed face gear to rotate, and finally the output shaft outputs the power; during gear shifting, the clutch is separated, the power source is disconnected, and the shifting fork is shifted to enable the synchronizing ring to be clamped with the other cylindrical gear; after gear shifting is completed, the clutch is closed, the power source is connected, power is output to the output shaft again, and the output rotating speed and the output torque synchronously change due to the fact that the gear ratio of the cylindrical gear and the face gear changes. The device has small structure size and light weight. Compared with the traditional cylindrical gear transmission, the face gear set can greatly reduce the occupied space of the gear, and the size and the weight are greatly reduced.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a face gear multi-gear speed change device comprises an input shaft, a clutch, a transmission shaft, a cylindrical gear set, a plurality of synchronous rings, a plurality of shifting forks, a face gear set and an output shaft;
the power source inputs power through the input shaft and then transmits the power to the transmission shaft through the clutch; the clutch is used for temporarily disconnecting power when the multi-gear transmission device shifts gears;
the cylindrical gear set comprises N cylindrical gears with different tooth numbers, the cylindrical gears are sleeved on the transmission shaft in a hollow mode, and the axial positions of the cylindrical gears are fixed;
when N is an even number, the number of the synchronizing rings and the number of the shifting forks are equal, and N/2 synchronizing rings and shifting forks are provided; the first synchronous ring is arranged between the first cylindrical gear and the second cylindrical gear, the second synchronous ring is arranged between the third cylindrical gear and the fourth cylindrical gear, and so on, and the Nth/2 th synchronous ring is arranged between the (N-1) th cylindrical gear and the Nth cylindrical gear;
when N is an odd number, the number of the synchronizing rings and the number of the shifting forks are equal and are (N + 1)/2; the first synchronous ring is arranged between the first cylindrical gear and the second cylindrical gear, the second synchronous ring is arranged between the third cylindrical gear and the fourth cylindrical gear, and so on, the (N-1)/2 th synchronous ring is arranged between the (N-2) th cylindrical gear and the (N-1) th cylindrical gear, and finally the (N +1)/2 th synchronous ring is arranged beside the Nth cylindrical gear;
a shifting fork is arranged above each synchronizing ring and is clamped into a groove of the synchronizing ring; the synchronous ring can move axially along the transmission shaft under the action of the shifting fork;
the transmission shaft is a spline shaft, and the synchronous ring is connected with the transmission shaft through a spline and rotates along with the transmission shaft;
the synchronous ring and the adjacent cylindrical gear are provided with mutually matched clamping structures, when the synchronous ring moves under the action of the shifting fork, the clamping structure of the synchronous ring and the adjacent cylindrical gear on one side takes effect, the synchronous ring and the cylindrical gear are fixed in the circumferential direction, and then the synchronous ring drives the cylindrical gear to rotate to transmit power; at the same time, all the synchronous rings are not clamped with the cylindrical gear or only one pair of synchronous rings is clamped with the cylindrical gear at most under the control of the external control mechanism;
the face gear set comprises N fixedly connected face gears with different tooth numbers, and the N cylindrical gears and the N face gears are correspondingly meshed in pairs to form different tooth ratios;
the face gear set is connected with the output shaft, power is transmitted to the transmission shaft from the input shaft through the clutch, the transmission shaft drives the synchronizing ring to rotate, the synchronizing ring drives the cylindrical gear to rotate through the clamping structure, the cylindrical gear drives the meshed face gear to rotate, and finally the output shaft outputs power; during gear shifting, the clutch is separated, the power source is disconnected, and the shifting fork is shifted to enable the synchronizing ring to be clamped with the other cylindrical gear; after gear shifting is completed, the clutch is closed, the power source is connected, power is output to the output shaft again, and the output rotating speed and the output torque synchronously change due to the fact that the gear ratio of the cylindrical gear and the face gear changes.
Preferably, the first specific form of the locking mechanism is:
a plurality of pin shafts are arranged on two end faces of the synchronizing ring along the circumferential direction; a plurality of through holes are formed in the cylindrical gear along the circumferential direction, and the diameter of each through hole is larger than that of the pin shaft on the synchronizing ring; the pin shafts can be completely inserted into the corresponding through holes, so that the synchronous ring is clamped with the cylindrical gear.
Preferably, the second specific form of the locking mechanism is:
inner conical friction plates are arranged on two end faces of the synchronous ring; an outer conical friction plate is arranged on the cylindrical gear; the taper angles of the inner conical friction plate and the outer conical friction plate are the same; the inner conical friction plate and the outer conical friction plate are matched by friction force to enable the synchronous ring to be clamped with the cylindrical gear.
Preferably, the taper angle of the inner conical friction plate and the taper angle of the outer conical friction plate are 10-90 degrees.
Preferably, the value of N ranges from 2 to 10.
Preferably, the face gear module of the outermost ring in the face gear set is greater than the face gear module of the innermost ring; the gear width of the outermost face gear in the face gear set is larger than that of the innermost face gear.
The invention has the following beneficial effects:
(1) the device has simple structure and is easy to process and manufacture. The number of parts is small, the processing is convenient, the cost is low, and the maintenance is convenient.
(2) The device has small structure size and light weight. Compared with the traditional cylindrical gear transmission, the face gear set can greatly reduce the occupied space of the gear, and the size and the weight are greatly reduced.
(3) The device has large transmission power. The face gear has large transmission contact ratio, so that large power can be transmitted.
(4) The device of the invention is convenient to assemble. The surface gear transmission has the characteristic of insensitivity to the axial installation error of the cylindrical gear, so the device has low requirement on the axial position precision of the cylindrical gear.
(5) The device of the invention has smooth gear shifting and no impact or small impact. Due to the adoption of the design of the synchronizing ring, the gear shifting can be realized only by shifting the synchronizing ring to be connected with the cylindrical gear during the gear shifting, and the synchronizing ring has smaller mass, so that the inertia during the gear shifting is small and the impact is smaller.
Drawings
Fig. 1 is a schematic diagram of the overall structure of the embodiment of the present invention.
Fig. 2 is a schematic view of a drive shaft component of an embodiment of the invention.
FIG. 3 is a schematic structural relationship diagram of a face gear and a cylindrical gear according to an embodiment of the present invention.
FIG. 4 is a schematic structural diagram of an embodiment of a cylindrical gear according to the present invention.
FIG. 5 is a schematic structural diagram of an embodiment of a synchronizer ring according to the present invention.
FIG. 6 is a schematic illustration of the position of the synchronizer ring in neutral according to an embodiment of the present invention.
FIG. 7 is a schematic diagram of a synchronizer ring position in first gear according to an embodiment of the present invention.
FIG. 8 is a schematic diagram of a synchronizer ring position in second gear according to an embodiment of the present invention.
FIG. 9 is a schematic diagram of a synchronizer ring position in third gear according to the embodiment of the present invention.
FIG. 10 is a schematic diagram of the position of the synchronizer ring in fourth gear according to the embodiment of the present invention.
FIG. 11 is a schematic structural view of a cylindrical gear according to a second embodiment of the present invention.
FIG. 12 is a schematic structural diagram of a synchronizer ring according to a second embodiment of the present invention.
In the figure: 1-an input shaft, 2-a clutch, 3-a transmission shaft, 4-a first cylindrical gear, 5-a second cylindrical gear, 6-a third cylindrical gear, 7-a third cylindrical gear, 8-a first synchronizing ring, 9-a second synchronizing ring, 10-a first face gear, 11-a second face gear, 12-a third face gear, 13-a fourth face gear, 14-an output shaft, 15-a first shifting fork and 16-a second shifting fork.
Detailed Description
The invention is further illustrated with reference to the following figures and examples.
The invention aims to overcome the defects in the prior art and provides a multi-gear speed changing device which is compact in structure, small in size, large in transmission power, easy to machine and manufacture and convenient to assemble and maintain.
A face gear multi-gear speed change device comprises an input shaft 1, a clutch 2, a transmission shaft 3, a cylindrical gear set, a plurality of synchronous rings, a plurality of shifting forks, a face gear set and an output shaft 14;
the input shaft 1 is connected with one end of the clutch 2, the other end of the clutch 2 is connected with the transmission shaft 3, and the power source inputs power through the input shaft 1 and then transmits the power to the transmission shaft 3 through the clutch 2; the clutch is used for temporarily disconnecting power when the multi-gear transmission device shifts gears;
the cylindrical gear set comprises N cylindrical gears with different tooth numbers, the cylindrical gears are sleeved on the transmission shaft in a hollow mode, and the axial positions of the cylindrical gears are fixed;
when N is an even number, the number of the synchronizing rings and the number of the shifting forks are equal, and N/2 synchronizing rings and shifting forks are provided; the first synchronous ring is arranged between the first cylindrical gear and the second cylindrical gear, the second synchronous ring is arranged between the third cylindrical gear and the fourth cylindrical gear, and so on, and the Nth/2 th synchronous ring is arranged between the (N-1) th cylindrical gear and the Nth cylindrical gear;
when N is an odd number, the number of the synchronizing rings and the number of the shifting forks are equal and are (N + 1)/2; the first synchronous ring is arranged between the first cylindrical gear and the second cylindrical gear, the second synchronous ring is arranged between the third cylindrical gear and the fourth cylindrical gear, and so on, the (N-1)/2 th synchronous ring is arranged between the (N-2) th cylindrical gear and the (N-1) th cylindrical gear, and finally the (N +1)/2 th synchronous ring is arranged beside the Nth cylindrical gear;
a shifting fork is arranged above each synchronizing ring and is clamped into a groove of the synchronizing ring; the synchronous ring can move axially along the transmission shaft under the action of the shifting fork;
the transmission shaft 3 is a spline shaft, and the synchronizing ring is connected with the transmission shaft 3 through a spline and rotates along with the transmission shaft 3;
the synchronous ring and the adjacent cylindrical gear are provided with mutually matched clamping structures, when the synchronous ring moves under the action of the shifting fork, the clamping structure of the synchronous ring and the adjacent cylindrical gear on one side takes effect, the synchronous ring and the cylindrical gear are fixed in the circumferential direction, and then the synchronous ring drives the cylindrical gear to rotate to transmit power; at the same time, all the synchronous rings are not clamped with the cylindrical gear or only one pair of synchronous rings is clamped with the cylindrical gear at most under the control of the external control mechanism;
the face gear set comprises N fixedly connected face gears with different tooth numbers, and the N cylindrical gears and the N face gears are correspondingly meshed in pairs to form different tooth ratios;
the face gear set is connected with the output shaft 14, power is transmitted to the transmission shaft 3 from the input shaft 1 through the clutch 2, the transmission shaft 3 drives the synchronizing ring to rotate, the synchronizing ring drives the cylindrical gear to rotate through the clamping structure, the cylindrical gear drives the meshed face gear to rotate, and finally the output shaft 14 outputs power; during gear shifting, the clutch 2 is separated, the power source is disconnected, and the shifting fork is shifted to enable the synchronizing ring to be clamped with the other cylindrical gear; after gear shifting is completed, the clutch 2 is closed, the power source is switched on, power is output to the output shaft 14 again, and the output rotating speed and the output torque are changed synchronously due to the change of the gear ratio of the cylindrical gear and the face gear.
Preferably, the first specific form of the locking mechanism is:
a plurality of pin shafts are arranged on two end faces of the synchronizing ring along the circumferential direction; a plurality of through holes are formed in the cylindrical gear along the circumferential direction, and the diameter of each through hole is larger than that of the pin shaft on the synchronizing ring; the pin shafts can be completely inserted into the corresponding through holes, so that the synchronous ring is clamped with the cylindrical gear.
Preferably, the second specific form of the locking mechanism is:
inner conical friction plates are arranged on two end faces of the synchronous ring; an outer conical friction plate is arranged on the cylindrical gear; the taper angles of the inner conical friction plate and the outer conical friction plate are the same; the inner conical friction plate and the outer conical friction plate are matched by friction force to enable the synchronous ring to be clamped with the cylindrical gear.
Preferably, the taper angle of the inner conical friction plate and the taper angle of the outer conical friction plate are 10-90 degrees.
Preferably, the value of N ranges from 2 to 10.
Preferably, the face gear module of the outermost ring in the face gear set is greater than the face gear module of the innermost ring; the gear width of the outermost face gear in the face gear set is larger than that of the innermost face gear.
The specific embodiment is as follows:
the present embodiment will be described by taking an example in which four spur gears are engaged with four face gears.
As shown in fig. 1 and 2, the input shaft 1 is connected with a clutch 2, and the clutch 2 is connected with a transmission shaft 3; the first cylindrical gear 4, the second cylindrical gear 5, the third cylindrical gear 6 and the fourth cylindrical gear 7 are sleeved on the transmission shaft 3 in an empty mode, and the axial positions of the first cylindrical gear, the second cylindrical gear, the third cylindrical gear and the fourth cylindrical gear are fixed; the first synchronizing ring 8 and the second synchronizing ring 9 are connected with the transmission shaft 3 through splines, the first synchronizing ring 8 is positioned between the first cylindrical gear 4 and the second cylindrical gear 5, and the second synchronizing ring 9 is positioned between the third cylindrical gear 6 and the fourth cylindrical gear 7; the face gear set is formed by fixedly connecting a first face gear 10, a second face gear 11, a third face gear 12 and a fourth face gear 13; the face gear set is connected with the output shaft 14; the first shifting fork 15 is arranged above the first synchronizing ring 8 and clamped into the groove of the first synchronizing ring 8; the second shifting fork 16 is arranged above the second synchronizing ring 9 and is clamped into a groove of the second synchronizing ring 9;
in fig. 3, a first face gear 10 meshes with the first cylindrical gear 4, a second face gear 11 meshes with the second cylindrical gear 5, a third face gear 12 meshes with the third cylindrical gear 6, and a fourth face gear 13 meshes with the fourth cylindrical gear 7.
Fig. 4 and 5 show an embodiment of a cylindrical gear 4 or 5 or 6 or 7 and a synchronizing ring 8 or 9, respectively, which is provided with a through hole along the circumferential direction and a pin shaft along the circumferential direction and is connected with a transmission shaft through a spline. The synchronizer ring can move axially along the transmission shaft, so that the pin shaft is inserted into the through hole of the cylindrical gear, the synchronizer ring is circumferentially fixed with the cylindrical gear, and the synchronizer ring can drive the cylindrical gear to rotate to transmit power.
The tooth numbers and modulus parameters of 4 cylindrical gears and 4 face gears designed in the embodiment are respectively shown in table 1:
TABLE 1 number of teeth and modulus of spur gears and face gears
| First gear | Second gear | Three-gear | Four-gear | |
| Face gear tooth number | 150 | 166 | 160 | 150 |
| Number of teeth of spur gear | 25 | 40 | 60 | 90 |
| Modulus of elasticity | 4mm | 3mm | 2.5mm | 2mm |
| Ratio of |
6 | 4.15 | 2.67 | 1.67 |
In fig. 6, the synchronizer rings 8 and 9 are located in the middle of the cylindrical gear, and are not connected with the cylindrical gear, and power is transmitted to the synchronizer rings through the input shaft 1, the clutch 2 and the transmission shaft 3, and no power is transmitted to the cylindrical gear, the face gear and the output shaft 14, so that the device is in a neutral state.
In fig. 7, the shifting fork 16 is kept in a disengaged state, the shifting fork 15 shifts the first synchronizing ring 8 to move rightwards, the pin shaft on the first synchronizing ring 8 is inserted into the through hole on the first cylindrical gear 4, and then the transmission shaft 3 can transmit power to the first cylindrical gear 4, the first face gear 10 and the output shaft 14 in sequence through the first synchronizing ring 8. The gear ratio of the first face gear 10 and the first cylindrical gear 4 is 6, namely the rotation speed is reduced by 6 times, the torque is increased by 6 times and then is output through the output shaft 14, and the device is in a first gear state, wherein the output rotation speed is minimum.
In fig. 8, the second shifting fork 16 is kept still, the first shifting fork 15 shifts the first synchronizing ring 8 to move leftward, the pin shaft on the first synchronizing ring 8 is inserted into the through hole on the second cylindrical gear 5, and the transmission shaft 3 can transmit power to the second cylindrical gear 5, the second face gear 11 and the output shaft 14 in sequence through the first synchronizing ring 8. The gear ratio of the second face gear 11 and the second cylindrical gear 5 is 4.15, namely the rotation speed is reduced by 4.15 times, the torque is increased by 4.15 times and then output through the output shaft 14, and the device is in a second gear state.
In fig. 9, the first shifting fork 15 is restored to a disengaged state, then the second shifting fork 16 shifts the second synchronizing ring 9 to move rightward, the pin shaft on the second synchronizing ring 9 is inserted into the through hole on the third cylindrical gear 6, and then the transmission shaft 3 can transmit power to the third cylindrical gear 6, the third face gear 12 and the output shaft 14 in sequence through the second synchronizing ring 9. The gear ratio of the third face gear 12 and the third cylindrical gear 6 is 2.67, namely the rotating speed is reduced by 2.67 times, the torque is increased by 2.67 times and then is output through the output shaft 14, and the device is in a third gear state.
In fig. 10, the first shifting fork 15 is kept still, then the second shifting fork 16 shifts the second synchronizing ring 9 to move left, the pin shaft on the second synchronizing ring 9 is inserted into the through hole on the fourth cylindrical gear 7, and then the transmission shaft 3 can transmit power to the fourth cylindrical gear 7, the fourth cylindrical gear 13 and the output shaft 14 in sequence through the second synchronizing ring 9. The gear ratio of the fourth face gear 13 and the fourth cylindrical gear 7 is 1.67, namely the rotation speed is reduced by 1.67 times, the torque is increased by 1.67 times and then is output through the output shaft 14, and the device is in a fourth gear state, wherein the output rotation speed is maximum.
So far, the concrete implementation principle of the invention is explained in full.
Referring to fig. 11 and 12, the invention also designs another embodiment for realizing the engagement of the cylindrical gear and the synchronizing ring, the synchronizing ring 8 and 9 are provided with inner conical friction plates, the cylindrical gears 4, 5, 6 and 7 are provided with outer conical friction plates, the synchronizing ring 8 or 9 and the cylindrical gears 4, 5, 6 and 7 are engaged through the friction of the friction plates, and further the power is transmitted, and the specific operation of gear shifting is the same as that of the embodiment one.
Claims (6)
1. A face gear multi-gear speed change device is characterized by comprising an input shaft, a clutch, a transmission shaft, a cylindrical gear set, a plurality of synchronous rings, a plurality of shifting forks, a face gear set and an output shaft;
the power source inputs power through the input shaft and then transmits the power to the transmission shaft through the clutch; the clutch is used for temporarily disconnecting power when the multi-gear transmission device shifts gears;
the cylindrical gear set comprises N cylindrical gears with different tooth numbers, the cylindrical gears are sleeved on the transmission shaft in a hollow mode, and the axial positions of the cylindrical gears are fixed;
when N is an even number, the number of the synchronizing rings and the number of the shifting forks are equal, and N/2 synchronizing rings and shifting forks are provided; the first synchronous ring is arranged between the first cylindrical gear and the second cylindrical gear, the second synchronous ring is arranged between the third cylindrical gear and the fourth cylindrical gear, and so on, and the Nth/2 th synchronous ring is arranged between the (N-1) th cylindrical gear and the Nth cylindrical gear;
when N is an odd number, the number of the synchronizing rings and the number of the shifting forks are equal and are (N + 1)/2; the first synchronous ring is arranged between the first cylindrical gear and the second cylindrical gear, the second synchronous ring is arranged between the third cylindrical gear and the fourth cylindrical gear, and so on, the (N-1)/2 th synchronous ring is arranged between the (N-2) th cylindrical gear and the (N-1) th cylindrical gear, and finally the (N +1)/2 th synchronous ring is arranged beside the Nth cylindrical gear;
a shifting fork is arranged above each synchronizing ring and is clamped into a groove of the synchronizing ring; the synchronous ring can move axially along the transmission shaft under the action of the shifting fork;
the transmission shaft is a spline shaft, and the synchronous ring is connected with the transmission shaft through a spline and rotates along with the transmission shaft;
the synchronous ring and the adjacent cylindrical gear are provided with mutually matched clamping structures, when the synchronous ring moves under the action of the shifting fork, the clamping structure of the synchronous ring and the adjacent cylindrical gear on one side takes effect, the synchronous ring and the cylindrical gear are fixed in the circumferential direction, and then the synchronous ring drives the cylindrical gear to rotate to transmit power; at the same time, all the synchronous rings are not clamped with the cylindrical gear or only one pair of synchronous rings is clamped with the cylindrical gear at most under the control of the external control mechanism;
the face gear set comprises N fixedly connected face gears with different tooth numbers, and the N cylindrical gears and the N face gears are correspondingly meshed in pairs to form different tooth ratios;
the face gear set is connected with the output shaft, power is transmitted to the transmission shaft from the input shaft through the clutch, the transmission shaft drives the synchronizing ring to rotate, the synchronizing ring drives the cylindrical gear to rotate through the clamping structure, the cylindrical gear drives the meshed face gear to rotate, and finally the output shaft outputs power; during gear shifting, the clutch is separated, the power source is disconnected, and the shifting fork is shifted to enable the synchronizing ring to be clamped with the other cylindrical gear; after gear shifting is completed, the clutch is closed, the power source is connected, power is output to the output shaft again, and the output rotating speed and the output torque synchronously change due to the fact that the gear ratio of the cylindrical gear and the face gear changes.
2. A face gear multiple speed change device as claimed in claim 1, wherein the first specific form of the locking mechanism is:
a plurality of pin shafts are arranged on two end faces of the synchronizing ring along the circumferential direction; a plurality of through holes are formed in the cylindrical gear along the circumferential direction, and the diameter of each through hole is larger than that of the pin shaft on the synchronizing ring; the pin shafts can be completely inserted into the corresponding through holes, so that the synchronous ring is clamped with the cylindrical gear.
3. A face gear multiple speed change device as claimed in claim 1, wherein the second specific form of the locking mechanism is:
inner conical friction plates are arranged on two end faces of the synchronous ring; an outer conical friction plate is arranged on the cylindrical gear; the taper angles of the inner conical friction plate and the outer conical friction plate are the same; the inner conical friction plate and the outer conical friction plate are matched by friction force to enable the synchronous ring to be clamped with the cylindrical gear.
4. A face gear multiple speed change device as claimed in claim 3, wherein the taper angle of said inner and outer conical friction plates is 10 to 90 °.
5. A face gear multiple speed transmission as claimed in claim 1, wherein N is between 2 and 10.
6. A face gear multiple speed change device as claimed in claim 1, wherein the face gear module of the outermost ring of said face gear set is greater than the face gear module of the innermost ring; the gear width of the outermost face gear in the face gear set is larger than that of the innermost face gear.
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| CN202111541229.2A CN114215890B (en) | 2021-12-16 | 2021-12-16 | Face gear multi-gear speed change device |
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| CN111377035A (en) * | 2020-03-27 | 2020-07-07 | 常州工学院 | Speed regulating system of bicycle |
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2021
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|---|---|---|---|---|
| US20050028627A1 (en) * | 2003-08-04 | 2005-02-10 | Yakov Fleytman | Gear reduction unit |
| JP2016050610A (en) * | 2014-08-29 | 2016-04-11 | オリエンタルモーター株式会社 | Face gear speed reducer |
| CN111268115A (en) * | 2020-02-27 | 2020-06-12 | 西安工业大学 | Face gear configuration coaxial dual-rotor variable speed transmission mechanism |
| CN111377035A (en) * | 2020-03-27 | 2020-07-07 | 常州工学院 | Speed regulating system of bicycle |
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| CN114215890B (en) | 2023-06-09 |
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