TW202019606A - A variable speed system divce. - Google Patents

Abstract

A variable speed system device in which a bearing-type clutch is arranged between a rotating shaft and a transmission wheel, the engagement for linkage and transmission or disengagement of the transmission wheel with the rotating shaft is controlled by the bearing-type clutch to complete the conversion of speed ratio of different transmission wheels, thereby obtaining different rotational speeds on an output rotating shaft, and having the advantages of being simplified and economic. Through this application, the speed changing requirement of existing non-CNC machine tools or non-variable frequency drive motor machine tool equipment and other speed changing system applications can be improved, the current control mode of manual conversion of speed changing transmission wheels, such as drilling and milling machines or machine tools that require conversion and matching of rotational speed ratio, or thread cutting operations of lathes, or speed-changing gear-shifting operations of gear boxes of motorcycles or motor vehicles. The simplified manual conversion of speed changing method is changed to more effective and user-friendly shift-lever displacement speed changing method.

Description

Variable speed system device

The invention of the present invention relates to the application technology of using the additional clutch device of the transmission wheel as the mechanism of the transmission system.

The present invention utilizes the principle of forward rotation and reverse braking of unidirectional bearings on the market. The design is changed and applied as a bearing clutch, and the combined application is a simple form and an economical characteristic transmission system.

Knowing the application examples on the market, taking the transmission device of a machine manufacturing machine tool other than CNC or non-inverter motor as an example, such as a drilling machine or a milling machine, etc., for a simpler tower wheel match, now using a belt application case as an example ;

As shown in Figure 17, through a single belt, matching on the transmission wheels of different diameters on the tower wheel, the motor closes the transmission wheel to change the speed, and then push out the belt on the tightening pulley to replace the single belt Switching the position of the transmission wheel of different diameters on the spot, and under the condition that the motor speed is fixed, different output shaft speeds are obtained to complete the required speed switching of different machining tools. Such control can achieve the output shaft conversion speed although simple Purpose, but does not have the time benefit of control. Due to frequent adjustment of variable speed control by personnel, the output value may be lost by 50% or more.

Commercially available gearboxes are usually geared with gears, with a fork or moving gear shaft Converting the transmission ratio between gears, using a lathe as an application example, we can obtain the different rotation speeds of the screw and the head of the lathe and the forward speed ratio of the cutting tool driven by the screw. The changeable range is not large, and it needs to be operated with an external crankset in a manpower conversion manner to operate a larger conversion interval. These are equipment facilities that can be expected to be improved by the present invention.

The technical problems to be solved by the present invention are:

The focus of the present invention is to provide a controllable system application device that changes the rotational speed. It is used with a mechanical bearing clutch to be used with a transmission wheel for shifting. It can be miniaturized and has a high load capacity. System installation.

The present invention is to provide a control of a bearing clutch device, which can easily control the opening and closing of a plurality of bearing clutches to control the transmission of the rotation kinetic energy between the rotating shaft and the transmission wheels connected at both ends of the bearing clutch , Or rotation kinetic energy disengagement for non-transferring control applications.

The technical means for solving the problems of the present invention are:

The technology cited in the present invention is mainly the principle of "one-way bearing" meshing interference linkage during forward rotation, free rotation non-interference linkage during reverse rotation, and the principle of unequal speed overrunning of inner and outer ring rings; The bearing cage of the one-way bearing and its internal rollers make a relative angular displacement, so that the timing of the interference linkage is controlled to become the bearing clutch of the present invention.

The "one-way bearing" braking principle applied in the present invention becomes the present invention after improvement The "bearing clutch 15" cited in the Ming Dynasty lists 4 types of 1A~4A and 5 types of a, b, c, d, and e in response to the so-called interference linkage operation phenomenon and the free rotation non-interference operation principle. The results are described; where a is the unique architecture design result applied by the present invention, and other b, c, d, and e are the universal functional architectures of commercially available one-way bearings, as described below, please refer to FIG. 6;

1A: Among them, the roller 15-8 is arranged between the bearing inner ring 15-5 and the bearing outer ring 15-12, the side wall of the bearing cage 15-7 contacts on one side, and the spring b15- on the other side 9 contact; the roller 15-8 can be rolled between the steel ball on the outer edge side of the bearing inner ring 15-5 and the roller outer edge b15-3, and the inner edge side of the bearing outer ring 15-12;

Result a: When the bearing cage stays in the above 1A: position, it is a free rotation state that does not interfere with both forward and reverse rotation;

2A: When the bearing retainer 15-7 is turned to the left by a relative angle, that is, the clutch lever 15-1 can be rotated and displaced by angle, the roller 15-8 is pushed by the spring b15-9 and is in contact with the bearing inner ring 15-5 The upper interference engagement latching flange b15-6 comes into contact (due to the right tangent flange), so that the roller 15-8 above the interference engagement latching flange b15-6 and the bearing outer ring 15-12 Form up and down contact interference state;

Result b: When the bearing cage stays in the above 2A: position, the outer ring 15-12 of the bearing rotates to the right, or the inner ring 15-5 of the bearing rotates to the left, and the roller 15-8 The rotating belt is away from the interference engagement locking flange b15-6, and all are in a free rotation state without interference;

Result c: When the bearing cage stays in the above 2A: position, the bearing outer ring 15-1 2 is to rotate to the left or the inner ring 15-5 of the bearing is to rotate to the right, the roller 15-8 is further rotated into the interference engagement locking flange b15-6, which is in the state of interference linkage.

3A: When in the 2A: position configuration, when the bearing inner ring 15-5 is actively positively rotating to the right, the bearing outer ring 15-12 is passively positive rotating to the right due to interference linkage;

Result d: When the rotation speed of the outer ring 15-12 of the bearing to the right is greater than the rotation speed of the inner ring 15-5 of the bearing to the right, it is in the form of overrunning, which is out of the interference linkage.

4A: When in the 2A: position configuration, when the bearing outer ring 15-12 is actively reversed to the left, the inner bearing ring 15-5 is passively reversed to the left due to interference;

Result e: When the reverse left rotation speed of the bearing inner ring ring 15-5 is greater than the reverse left rotation speed of the bearing outer ring ring 15-12, it is in the form of overrunning and disengages from the interference linkage.

The present invention is a transmission system device, and the cited technology is mainly to regard the bearing inner ring 15-5 of the above application example as a rotating shaft, and the bearing outer ring 15-12 as a transmission wheel, and in this way Control the timing of the interlocking control of the interference between the rotating shaft and each transmission wheel in an effective and simple way.

The present invention is a transmission system device. The technical method is to provide a rotating shaft with a central inner shaft hole, and a control inner shaft 16 is arranged in the central inner shaft hole, which can slide up and down to the center of the rotating shaft In the inner shaft hole, the control inner shaft 16 and the rotating shaft are connected to make the two have a synchronous rotation function, and then the control inner shaft 16 is provided with a locking follower track 16-2 and a disengaging follower track 16-3 to make the control The radial movement of the shaft 16 can drive the bearing cage 15-7 in the bearing clutch 15 described in [0010] to make a relative angle of rotation The associated control of the opening and closing interference.

The present invention is a transmission system device in which the coupling hole B16-1 of the control inner shaft 16 utilizes the coupling with the axial transmission coupling disk 8 to make an axial sliding connection with the rotating shaft and rotate synchronously with the rotating shaft; 4 Follow the position limiting slot plate 5-1 to make positioning inching, lead the control inner shaft 16 to make positioning inching movement synchronously, and control the follower wheel track 16-2 for locking provided on the inner shaft 16 , And the difference in position and angle of the follower track 16-3 for disengagement, the mechanism-type stable and integrated synchronous control of a plurality of bearing clutches is obtained, and it becomes a device for using the speed change mechanism of the speed change system.

The invention is a variable speed system device, which can be matched with a multi-style transmission wheel combination, which is suitable for the control of belt wheels, timing belt wheels, gears, friction wheels, transmission shaft connecting rods and the like.

Compared with the prior art, the present invention has the following effects:

Can provide another type of shifting method for various types of equipment as a shifting scheme, avoiding the unproductive operation of manual conversion of the above applications such as drilling machines and milling machines, and liberating the hands and mental attention of frequent manual shifting of gear shifting. Pay more attention to the production quality, performance and output of the machine tool control and the operational safety of the personnel; let non-CNC CNC machine tools, or machine tools that do not use expensive inverter motors, and mechanical mechanisms and facilities that require variable-speed gearbox equipment, It has a speed control system that can shorten the time and be more efficient, to quickly change the main machine shaft production speed of the machine tool production or a variety of gearboxes for simple control of a transmission system.

It is divided into: [0024] letter code: and [0025] digital code:

Letter code:

A‧‧‧Right input shaft A

A1‧‧‧Low speed ratio rotation control output transmission wheel A

A11‧‧‧Low speed wheel belt

A12‧‧‧Low speed ratio input drive wheel A

A2‧‧‧ Medium speed ratio rotation control output transmission wheel A

A21‧‧‧Medium speed belt

A22‧‧‧ Medium speed ratio rotating input transmission wheel A

A3‧‧‧High-speed ratio rotation control output transmission wheel A

A31‧‧‧High-speed wheel belt

A32‧‧‧High-speed ratio input drive wheel A

B‧‧‧Right input shaft B

B1‧‧‧Low speed ratio rotation control output transmission wheel B

B11‧‧‧Low speed ratio rotating input transmission wheel B

B2‧‧‧ Medium speed ratio rotation control output transmission wheel B

B21‧‧‧ Medium speed ratio rotating input transmission wheel B

B3‧‧‧High-speed ratio rotation control output transmission wheel B

B31‧‧‧High-speed rotating input transmission wheel B

C‧‧‧Speed-increasing rotary input shaft

C1‧‧‧Low speed ratio rotation control input transmission wheel

C11‧‧‧Low speed ratio rotating output transmission wheel

C2‧‧‧ Medium speed ratio rotation control input transmission wheel

C21‧‧‧ Medium speed ratio rotating output transmission wheel

C3‧‧‧High-speed ratio rotation control input transmission wheel

C31‧‧‧High-speed rotating output transmission wheel

D‧‧‧left output shaft

Digital coding:

1‧‧‧rotation input shaft

1-1‧‧‧Keyway

2‧‧‧rotating output shaft

2-1‧‧‧Control inner shaft moving slot a

2-2‧‧‧Keyway a

2-3‧‧‧Bearing limit flange a

2-4‧‧‧ Clutch lever yield slot a

2-5‧‧‧rotation shift shaft

2-6‧‧‧ Center shaft hole a

3‧‧‧Drive wheel

4‧‧‧shift lever

5‧‧‧Main support plate

5-1‧‧‧Position limiting slot plate

6‧‧‧Spring a

7‧‧‧shift ring

8‧‧‧Axial variable speed coupling disc

8-1‧‧‧Coupling hole A

8-2‧‧‧ Output axial variable speed coupling disc

8-3‧‧‧Variable speed axial coupling disc

9‧‧‧Fixed rear axle

10‧‧‧Handle movable front axis

11‧‧‧Cam Follower

12‧‧‧Rotation axis rotation direction sign

13‧‧‧Radial thrust ball bearings

14‧‧‧Limiting sleeve

15‧‧‧bearing clutch

15-1‧‧‧clutch lever

15-2‧‧‧clutch follower wheel

15-3‧‧‧Ball and roller rolling outer edge b

15-4‧‧‧ Clutch lever yield slot b

15-5‧‧‧Bearing inner ring

15-6‧‧‧Interference engagement locking flange b

15-7‧‧‧bearing cage

15-8‧‧‧Roller

15-9‧‧‧spring b

15-10‧‧‧steel ball

15-11‧‧‧Following wheel center shaft bolt

15-12‧‧‧Bearing outer ring

15-13‧‧‧Ball limit arc ring b

15-14‧‧‧Bearing limit lock cover

15-15‧‧‧key 1b

15-16‧‧‧Key 2b

15-17‧‧‧pin hole

15-18‧‧‧Inner edge side keyway b

15-19‧‧‧Key slot on outer edge b

15-20‧‧‧ Rolling inner edge of steel ball and roller b

16‧‧‧Control inner shaft

16-1‧‧‧Coupling hole B

16-2‧‧‧ Follower track for locking

16-3‧‧‧ Follower wheel track for disengagement

16-4‧‧‧ linkage pin

17‧‧‧Bearing inner ring integral rotating shaft

17-1‧‧‧Control inner shaft moving slot c

17-2‧‧‧‧Ball and roller rolling outer edge c

17-3‧‧‧Bearing limit flange c

17-4‧‧‧ Clutch lever yield slot c

17-5‧‧‧Integrated bearing inner ring

17-6‧‧‧Interference engagement locking flange c

17-7‧‧‧Steel ball limit arc ring c

17-8‧‧‧Integrated bearing inner ring rings

17-9‧‧‧One-piece bearing inner ring part arrangement

17-10‧‧‧Keyway c

17-11‧‧‧ Center shaft hole c

18‧‧‧Bearing outer ring integrated drive wheel

18-1‧‧‧ Rolling inner edge of steel ball and roller d

18-2‧‧‧Steel ball limit arc ring d

18-3‧‧‧Limited locking cover for transmission wheel

19‧‧‧Radial roller thrust bearing

20‧‧‧Speed-increasing transmission wheel combination

21‧‧‧fixing screw

22‧‧‧shift shift lever

23‧‧‧Shifting bidirectional ring

Figure 1: The application of a transmission system device of the present invention, the belt drive wheel 3-speed transmission and transmission control Schematic diagram of the operation of the handle device. A: Front view of the 3-speed transmission of the belt drive wheel.

B: Side view of the 3-speed transmission of the belt drive wheel.

Figure 2: This is the upper side perspective view of the belt transmission wheel 3-speed transmission device of the transmission system device of the present invention.

Fig. 3: The application of the transmission system device of the present invention, a front view and a side perspective view of a belt drive wheel 3-speed transmission device. A: The top perspective view of the 3-speed transmission of the belt drive wheel.

B: The bottom perspective view of the 3-speed transmission of the belt drive wheel.

Figure 4: Exploded illustration of the belt transmission wheel 3-speed transmission device for the application of the transmission system device of the present invention.

A: The exploded front view of the belt drive wheel with 3 speeds.

B: The three-dimensional exploded three-dimensional structure diagram of the belt drive wheel.

Fig. 5: The transmission system device of the present invention, a 3-speed transmission cross-sectional view of a belt drive wheel and a component installation diagram.

A: Front sectional view of the 3-speed transmission of the belt drive wheel.

B: Installation and configuration diagram of the bearing clutch 15 for 3-speed transmission of the belt drive wheel.

Fig. 6: The bearing clutch of the transmission system device of the present invention.

F: a top view of the bearing clutch 15.

G: Front view of the bearing clutch 15.

H: is a top perspective line drawing of the bearing clutch 15.

I: It is the E-E sectional view of the bearing clutch 15.

J: is a perspective perspective line drawing of the bearing clutch 15.

K: is a perspective perspective line drawing of the bearing clutch 15.

7 is an exploded view of the bearing clutch of the transmission system device of the present invention.

8 is a cross-sectional view of the bearing clutch of the transmission system device of the present invention at various angles.

FIG. 9 is a diagram showing the control relationship between the bearing cage of the bearing clutch of the transmission system device of the present invention and the control inner shaft.

A: It is a top view of the bearing cage of the bearing clutch and the control inner shaft.

B: Schematic diagram of the three-dimensional assembly control of the bearing cage of the bearing clutch and the control inner shaft.

Fig. 10 is a diagram showing the control relationship between the bearing cage of the bearing clutch of the transmission system device of the present invention, the rotary output shaft and the control inner shaft.

A: It is the top view of bearing cage and control inner shaft.

B: It is a perspective view of the bearing cage and the control inner shaft.

C: Another perspective view of the bearing cage and the control inner shaft.

11 is a schematic diagram of the combination of the bearing cage of the bearing clutch of the transmission system device of the present invention and the output shaft of the inner ring of the integrated clutch.

F: One-piece rotating shaft 17 on one-piece bearing inner ring complete arrangement 17-8.

F1: It is the integral rotating shaft 17 on the part 17-9 of the inner ring of the integral bearing.

G: is a front perspective view of the bearing outer ring 15-12.

H: Front view of bearing outer ring 15-12.

I: It is a perspective view of the bearing outer ring 15-12.

J: It is a perspective view of the bearing retainer on the integral bearing inner ring ring 17-8 combined with the integral rotating shaft 17.

J1: The bearing cage on the integral bearing inner ring ring 17-8 is combined into one Front view of the rotating shaft 17.

J2: Front perspective view of the bearing retainer on the integral arrangement of the integral bearing inner ring ring 17-8 combined with the integral rotating shaft 17.

K: is a perspective view of the bearing limit locking cover.

K1: Front view of the bearing limit locking cover.

K2: Front perspective view of the bearing limit locking cover.

FIG. 12 is a schematic diagram comparing the rotary output shaft of the transmission system device of the present invention with the output shaft of the inner ring of the integrated clutch. J: Bottom view of the integral rotating shaft 17 of the bearing inner ring.

J3: It is a perspective view of the integral rotating shaft 17 of the bearing inner ring.

K: bottom view of the rotating output shaft 2.

K3: is a perspective view of the rotating output shaft 2.

13 is a schematic diagram of a combined component of a transmission wheel of the transmission system device of the present invention and a bearing cage of a bearing clutch, which is combined into a transmission wheel clutch.

M: It is a combination diagram of the bearing clutch.

M1: Front view of the bearing clutch combination.

M2: is a perspective view of a bearing clutch combination.

L: is a perspective view of the components of the bearing clutch.

L1: is a perspective view of the bearing outer ring integral transmission wheel 18 of the bearing clutch.

L2: A perspective view of the bearing cage assembly of the bearing clutch.

L3: is a perspective view of the transmission wheel limit locking cover 18-3 of the bearing clutch.

14 is a schematic diagram of the combination of the transmission wheel clutch and the output shaft of the inner ring of the integrated clutch and the explosion of the transmission system device of the present invention.

N: It is the combination of the output shaft of the inner ring of the integrated clutch and the transmission wheel clutch.

N1: Front view of the output shaft of the inner ring of the integrated clutch and the transmission wheel clutch.

N2: a perspective view of the output shaft of the inner ring of the integrated clutch and the transmission wheel clutch.

O: Exploded view of the output shaft of the inner ring of the integrated clutch and the transmission wheel clutch.

O1: a side view of the bearing outer ring integral drive wheel 18.

O2: Side view of the integral rotating shaft 17 of the bearing inner ring.

O3: Side view of the locking cap 18-3 for the transmission wheel limit.

O4: Exploded perspective view of the output shaft of the inner ring of the integrated clutch and the transmission wheel clutch.

15 is a schematic diagram of the operation of the gear transmission wheel 6-speed shift and shift control lever device for the application of a shift system device of the present invention.

A: A perspective view of a 6-speed speed change system of a gear transmission wheel applied to a speed change system device.

B: Front view of a 6-speed transmission system of gear transmission wheels applied to a transmission system device.

C: Side view of a 6-speed gear shifting system for gear transmission wheels applied to a gear shifting system device.

Fig. 16 is a schematic diagram of the combined position of the bearing clutch of the gear transmission wheel 6-speed transmission and the axial radial roller thrust bearing for the conversion of the speed-increasing shaft for the application of a transmission system device of the present invention.

Figure 17: Schematic diagram of a commercially available general pulley speed change device.

A component description of a transmission system, mainly including a rotating shaft, a transmission wheel, and Bearing clutch 15;

The rotating shaft includes: a rotating input shaft 1, a rotating output shaft 2, and a rotating transmission shaft 2-5, etc.; the transmission wheel includes: ((transmission wheel A, transmission wheel B, transmission wheel C) Codes such as transmission wheel A1 or transmission wheel A22), and transmission wheel 3; including pulleys, timing pulleys, and various types of gears;

The bearing clutch 15 includes a bearing inner ring 15-5, a bearing outer ring 15-12, a bearing cage 15-7 and its internal components.

For a transmission system device, please refer to the embodiments of FIGS. 1, 2, 3, 4, and 5. The present invention is to provide a transmission system application device for a transmission control machine tool device or a transmission system device assembly using a belt drive wheel as an embodiment;

As shown in the exploded view of FIG. 4, the main components include an upper and a lower main support plate 5, and a group of rotating shafts with two shafts marked as right rotations, which are divided into a rotating input shaft 1 and a rotating output shaft 2, and a plurality of transmission wheels 3. Composed of multiple bearing clutches 15;

The rotation shaft has a rotation input shaft 1 sleeved into the transmission wheels A12, A22, A32, and the radial thrust ball bearings 13 and the main support plate 5 are positioned on both sides to freely rotate; in addition, there is a rotation output on the right side Shaft 2, put the bearing clutch 15 on the shaft, and then put the transmission wheels A1, A2, A3 on each side, and then use the radial thrust ball bearings 13 and the main support plate 5 on both sides to make a freely rotatable positioning. Then put the belts A11, A21, A31 into the associated transmission wheel set; then insert the control inner shaft 16 (see Figure 5) in the central inner shaft hole a2-6 of the rotary output shaft 2 and insert it with the interlocking pin 16-4 Connect the coupling hole A above the axial shift coupling disc 8 8-1 and the control inner shaft moving groove a2-1 on the rotary output shaft 2 and the coupling hole B16-1 on the control inner shaft 16 are connected.

As shown in detail in Figure 1, the rotary input shaft 1 has a low speed ratio rotary input transmission wheel A (A12) fixed to the keyway 1-1, a medium speed ratio rotary input transmission wheel A (A22), and a high speed ratio rotary input transmission wheel Wheel A (A32); and the low speed ratio rotation control output transmission wheel A (A1) above the bearing clutch 15 (see FIG. 5) provided on the rotary output shaft 2 and the medium speed ratio rotation control output transmission wheel A (A1) A2), and high-speed ratio rotation control output transmission wheel A (A3);

The above-mentioned low-speed ratio rotation input transmission wheel A (A12) and the low-speed ratio rotation control output transmission wheel A (A1) are normally connected and driven by the low-speed wheel belt A11;

The intermediate speed ratio rotation input transmission wheel A (A22) and the intermediate speed ratio rotation control output transmission wheel A (A2) are normally connected and driven by the intermediate speed belt A21;

The high-speed ratio rotation input transmission wheel A (A32) and the high-speed ratio rotation control output transmission wheel A (A3) are normally connected and driven by a high-speed wheel belt A31;

Please refer to FIG. 5 first, where a bearing clutch 15 is provided between all the transmission wheels disposed above the rotary output shaft 2 and the rotary output shaft 2; a control inner shaft 16 is provided in the shaft hole a2-6 in the center of the rotary output shaft 2 , The control inner shaft 16 has a coupling hole B16-1, which is related to the control inner shaft moving groove a2-1 above the rotary output shaft 2 through the linkage pin 16-4 shown in FIG. The diameter of the circular hole of the coupling hole B16-1 and the width of the long groove that controls the inner shaft moving groove a2-1 and the size of the outer diameter of the interlocking pin 16-4 The same), so that the control inner shaft 16 and the rotary output shaft 2 rely on the linkage pin 16-4 to have a limited connection of synchronous rotation; then through the linkage pin 16-4 and the coupling hole A8-1 above the axial shift coupling disk 8 Combination (the above two, the outer diameter of the linkage pin 16-4 is the same size as the diameter of the circular hole of the coupling hole A8-1), so the axial shift coupling disk 8 is provided with both the rotary output shaft 2 and the control inner shaft 16 Restricted connection of synchronous rotation; and because the control inner shaft moving slot a2-1 above the rotation output shaft 2 is a long slot hole, the interlocking pin 16-4 can slide in the long slot hole, so the axial speed is changed The coupling disc 8 and the control inner shaft 16 can slide within the slot of the control inner shaft moving slot a2-1;

Please refer to FIG. 3B: the shifting handle 4 slides on the position-limiting slot plate 5-1, the front axis 10 of the handle is connected to the long slot in the shift ring 7, and the fixed rear axis 9 is used as Fixed swing axis, in which the shift ring 7 draws the axial shift coupling disc 8 on both sides through the cam follower 11, and the spring a6 exerts force on the handle front axis 10 and the position limiting groove plate 5- The rear side of 1 causes the shifting handle 4 to be attached to the front guide groove of the position restricting groove plate 5-1, so that the displacement of the fixed value of the inching property can be made, and the displacement of the fixed value of the inching property The size is converted into a bearing-type clutch 15 that controls the locking follower track 16-2 above the inner shaft 16 and the disengaging follower track 16-3 relative to the rotating output shaft 2 above and the transmission wheel (please (Refer to Figure 5) Design value of the interference linkage opening and closing curve (see Figure 9B for the follower wheel track 16-2 for the phase-locking lock and the follower wheel track 16-3 for the disengagement), according to which, the shift lever 4 is relative to the position limiting groove The fixed displacement of the plate 5-1 represents the low-speed transmission wheel, or the medium-speed transmission wheel, or the high-speed transmission on the bearing clutch 15 above the rotating output shaft 2 The control point where the wheel is controlled to be turned on or off;

Please refer to FIG. 1, when the rotary input shaft 1 starts to have rotational speed kinetic energy, the low speed ratio rotation input transmission wheel A (A12) links the low speed wheel belt A11, and the medium speed ratio rotation input transmission wheel A (A22) links the intermediate speed The wheel belt A21 and the high-speed ratio rotation input transmission wheel A (A32) link the high-speed wheel belt A31 to rotate simultaneously, driving the low-speed ratio rotation control output transmission wheel A (A1), and the medium-speed ratio rotation control output transmission wheel A (A2) , And the high-speed ratio rotation control output transmission wheel A (A3), which also rotates synchronously, at this time the speed gear is marked next to the shift handle 4 in the front view and side view of FIG. 1;

(The following description of the positions marked as 0, A1, A2, A3, please refer to the part numbers shown in Figures 1, 4, 5, 6, 7 and 9):

The position marked as 0 in Fig. 1 means: as shown in Figs. 5 and 9, the rotary output shaft 2 does not move, because the clutch lever 15-1 of the bearing clutch 15 has not yet been activated, and the transmission wheel A1 The clutch lever follower wheels 15-2 of the bearing clutch 15 of A2 and A3 are on the follower wheel track 16-3 for disengagement;

The meaning of the position marked A1 in Fig. 1 is: as shown in Figs. 3, 5, 6, and 9, the shifting handle 4 is shifted to this position by a fixed distance, and the inner shaft 16 is pulled to control the downward movement, and the follower wheel track 16 is locked by 2 Start the clutch follower wheel 15-2 of the bearing clutch 15 to urge the bearing cage 15-7 and the driven roller 15-8 to start the interference linkage, so that the low speed ratio rotation control output transmission wheel A (A1) starts to be transmitted The rotational kinetic energy given by the low-speed wheel belt A11 generates a low-speed specific rotational speed for the rotary output shaft 2;

The meaning of the position marked as A2 in Figure 1 means: as shown in Figures 3, 5, and 9, the shifting handle 4 is shifted to this position by a fixed distance, and the inner shaft 16 is pulled to control the downward movement, which is started by the locking follower track 16-2 The clutch lever of the bearing clutch 15 follows the wheel 15-2 and starts to interfere with the linkage, so that the intermediate speed ratio rotation control output transmission wheel A (A2) starts to transmit the intermediate speed ratio speed of the rotational kinetic energy given by the intermediate speed belt A21, process The rotational kinetic energy input by the low speed ratio rotation control output transmission wheel A (A1) of the Central Plains does not need to be withdrawn. The rotation speed of the rotary output shaft 2 is increased by the medium speed ratio rotation control output transmission wheel A (A2), which is changed from the original low speed to The output shaft 2 rotates at a medium speed, so the bearing clutch 15 of the low speed ratio rotation control output transmission wheel A (A1) makes a rotation overtaking action;

The meaning of the position marked A3 in Fig. 1 means: as shown in Figs. 3, 5, and 9, the shifting handle 4 is shifted to this position by a fixed distance, and the inner shaft 16 is pulled to control the downward movement again, and the follower track 16-2 is locked Start the clutch lever 15-2 of the bearing clutch 15 and start the interference linkage, so that the high-speed specific rotation control output transmission wheel A (A3) starts to transmit the high-speed specific speed of the rotational kinetic energy given by the high-speed wheel belt A31, the original low speed in the process The rotational kinetic energy input by the specific rotation control output transmission wheel A (A1) and the intermediate speed ratio rotation control output transmission wheel A (A2) does not need to be exited, and the rotary output shaft 2 is improved by the high speed ratio rotation control output transmission wheel A (A3) The rotation speed of the shaft is changed from the original middle rotation speed to the high-speed rotation output shaft 2. Therefore, the bearing clutch 15 that controls the output transmission wheel A (A2) for the middle speed ratio rotation control also performs an overrunning action.

For a control component of a variable speed system device, please refer to Figures 6, 7, and 8, this The main control component of the inventive transmission system device is the bearing clutch 15, which provides the advantages of convenient design, assembly and maintenance in the form of bearings, as shown in Figures 7 and 8;

The bearing clutch 15 is composed of four parts: the bearing inner ring 15-5, the bearing outer ring 15-12, the bearing retainer 15-7, and the bearing limit locking cover 15-14.

Above the bearing inner ring 15-5, there is a steel ball and roller rolling outer edge b15-3, a clutch lever yield groove b15-4, an interference engagement locking flange b15-6, and a steel ball limit arc ring b15-13, and the inner edge side keyway b15-18, etc., wherein the interference engagement locking flange b15-6 is a beveled tangent flange generated from the outer circle tangent of the steel ball and roller rolling outer edge b15-3, following the bearing inside The circle center of the ring 15-5 is given a plurality of slanted tangent flanges arranged at an equal angle within a certain installation angle to become an interference engagement locking flange b15-6;

Above the bearing outer ring 15-12, there are the key groove b15-19 on the outer edge side of the steel ball limit arc ring b15-13 and the inner edge b15-20 of the steel ball and roller rolling, as shown in Figures 6 and 7 1b15-15 and key 2b15-16 are a set of matching keys for fixing the outer edge side key slot b15-19. The key 1b15-15 and key 2b15-16 are interlocked with screws, which can drive the transmission wheel and the bearing clutch 15 Fix and interlock the bearing limit locking cover 15-14 with the bearing outer ring 15-12, where the key 1b15-15 has a screw hole and the key 2b15-16 has an internal thread;

Among them, above the bearing cage 15-7, there are various parts installation slots, which are installed with a plurality of Set of rollers 15-8, and spring b15-9 (can be a spring of spring type or spiral structure), and steel ball 15-10, and clutch lever 15-1, and clutch lever follower 15-2 Install the follower wheel center shaft bolt 15-11 on the clutch lever 15-1;

Please refer to FIG. 6I: SECTION: EE. This embodiment is a sectional view of the bearing clutch 15 in which the interference engagement locking flange b15-6 is a sloped flange facing the right side, and there is a roller at a unit distance on the right side. 15-8, a spring b15-9 on the right side of the roller 15-8 is preloaded to contact the cylindrical surface of the roller 15-8, the spring b15-9 is limited by the shape feature of the bearing cage 15-7, The interference engagement locking flange b15-6, the roller 15-8 and the spring b15-9 follow the center of the circle of the bearing inner ring 15-5 to be arranged at equal angles, and are not provided on the bearing cage 15-7 A clutch lever 15-1 is provided at the roller and the spring, and then a clutch lever follower wheel 15-2 is installed above it, and then mounted on the clutch lever 15-1 with a follower wheel center shaft bolt 15-11; Then, install the assembly of the clutch lever 15-1 in the clutch lever shift groove b15-4 on the bearing inner ring 15-5, and surround a plurality of bearing cages 15-7 around the bearing inner ring 15- 5 Combine into a circle, align with the pin holes 15-17 as shown in Figure 7 and insert the pin to fix it;

When the bearing cage 15-7 is in the position shown in FIG. 6I: SECTION: EE, in which the bearing cage 15-7 leads the roller 15-8 installed within its limit to disengage from the interference engagement locking flange b15-6 area, When the bearing outer ring ring 15-12 or the bearing inner ring ring 15-5 is in any rotating form, the roller 15-8 in the bearing cage 15-7 is displayed in a free rolling form (roller 15-8 and bearing The outer ring 15-12 is continuous rolling The roller 15-8 and the bearing inner ring 15-5 are in a fixed position rolling form; the outer diameter of the roller 15-8 is slightly smaller than the outer edge of the bearing inner ring 15-5 and the bearing outer ring 15-12 The radius of the flange), so there is no linkage between the inner ring 15-15 of the bearing and the outer ring 15-12 of the bearing;

Assuming the state is as follows, the left-handed clutch lever follower 15-2 is applied to force the clutch lever 15-1 to move the bearing cage 15-7 to the left, and the left-handed displacement is a relative angle. The linked spring b15-9 pushes the roller 15-8 to touch Interference engagement latching flange b15-6, wherein the spring b15-9 elastic preload adjustment causes each roller 15-8 in the bearing cage 15-7 to be convex with the inclined surface of the interference interference latching flange b15-6 Marginal energy can be completely closed and contact interference under nearly equal pressure;

When the outer ring ring 15-12 of the bearing rotates counterclockwise relative to the inner ring ring 15-5 of the bearing, that is, the rotation speed of the outer ring ring 15-12 of the bearing is greater than the inner ring ring 15-5 of the bearing, it is a form of full contact interference linkage, in which the roller 15 -8 in the form of interference contact, and the interference form of the bearing outer ring 15-12 and the bearing inner ring 15-5 to limit the slip is displayed; at this moment, the bearing outer ring 15-12 is opposite to the bearing inner ring 15- 5 is the fully meshing and locking linkage;

According to the above description, when the inner ring ring 15-5 of the bearing rotates counterclockwise relative to the outer ring ring 15-12 of the bearing, that is, when the rotation speed of the inner ring ring 15-5 of the bearing is greater than that of the outer ring ring 15-12 of the bearing, the roller 15-8 is When the spring b15-9 is pushed by the elastic preload, the speed of the inner ring 15-5 of the bearing is accelerated, so that only the outer ring 15-12 of the bearing has contact rolling friction with the roller 15-8, the roller 15 -8 Start self-rotation, and do not interfere with interference interference engagement locking convex The edge b15-6 makes the interference friction force against the bearing inner ring 15-5 lost, and the preload elastic force of the spring b15-9 becomes a reaction force to compress the spring b15-9, so that the bearing inner ring 15-5 Into a freely accelerated rotation state, becoming a disengaged or transcended form;

As described above, by applying force to the different rotation directions of the clutch lever follower 15-2, the bearing inner ring ring 15-5 and the bearing outer ring ring 15-12 can be changed as a result of disengagement interference or meshing and locking linkage. According to this control method, a plurality of bearing clutches 15 are organized and combined, and the bearing clutch 15 is arranged between the rotating shaft and the transmission wheel 3, and can be applied as a module of a transmission system.

Preferably, for a transmission system device, please refer to FIGS. 15 and 16 embodiments. The present invention is to provide a transmission system application of a machine tool equipment or a transmission system equipment assembly of a 3-axis 6-speed transmission control system in the form of a gear for the transmission wheel 3 Device

As shown in Fig. 15, the main components include an upper and a lower main support plate 5, and a set of rotating shafts divided into a rotating input shaft 1 with a right rotating shaft rotation direction of 12 and a rotating output shaft 2 with a left rotating shaft rotation direction of 12. The rotating shaft 2-5 with the rotation direction of 12 on the right rotating shaft, and each shaft has a plurality of transmission wheels 3 and a plurality of bearing clutches 15;

As shown in Fig. 16, the rotating shaft has a rotating input shaft 1 sleeved into the transmission wheels B11, B21, B31, and the radial thrust ball bearings 13 and the main support plate 5 on both sides are freely rotatable (the rotating shaft The installation of the radial thrust ball bearing 13 is the same as shown in Figures 4 and 5; the following shafts are the same); In addition, there is a rotating output shaft 2 on the middle side, and a bearing clutch 15 is installed on the shaft, which is the same as the rotating input shaft 1 The transmission wheels correspond to area B1, area B2, and area B3. The transmission wheels C11, C21, and C31 that are fixed in the key slot of the rotating output shaft 2 correspond to the transmission wheels of the rotating transmission shaft 2-5, and the corresponding position areas of the rotating transmission shaft 2-5 are C1, C2, and C3. The bearing clutch 15 is installed in the zone, and the sleeve 14 (as shown in the installation diagram of FIG. 4) is used to complete the alignment of the assembly dimensions of the shaft drive wheels; as shown in FIG. 15, there are The speed-increasing transmission wheel assembly 20, according to the gear ratio of the embodiment, the rotation speed of the rotating transmission shaft 2-5 is 3.45 times that of the rotating input shaft 1. As shown in FIG. 16, the middle-side speed-increasing gear is set at the radial roller thrust The bearing 19 is fixed by the fixing screw 21, so that it has nothing to do with the rotation speed of the rotating output shaft 2; back to FIG. 15, then insert each into the inner shaft holes of the rotating output shaft 2 and the rotating transmission shaft 2-5 as shown in the figure 9 shows the follower wheel track 16-2 for locking with different sizes and touch design, and the control inner shaft 16 for the follower wheel track 16-3 for disengagement, and the remaining coupling methods are the same as described in [0018];

Please refer to FIG. 15 for a detailed description of each transmission wheel configuration, in which the rotary input shaft 1 has a low-speed ratio rotary input transmission wheel B (B11) fixed to the keyway 1-1, and a medium-speed ratio rotary input transmission wheel B (B21), And high-speed ratio rotation input transmission wheel B (B31); and low-speed ratio rotation control output transmission wheel B (B1) provided above the rotary output shaft 2 corresponding to the low-speed ratio rotation input transmission wheel B (B11), and corresponding to the medium-speed ratio rotation The input transmission wheel B (B21)'s medium-speed ratio rotation control output transmission wheel B (B2), and the corresponding high-speed ratio rotation input transmission wheel B (B31) high-speed ratio rotation control output transmission wheel B (B3); The specific rotation output transmission wheel C11, the intermediate speed ratio rotation output transmission wheel C21, and the high speed ratio rotation output transmission wheel C31 are synchronously fixed in sequence on the key slot of the rotary output shaft 2; and on the rotary transmission shaft 2-5 Corresponding location areas C1, C2, and C3 are installed above the bearing clutch 15, and the low-ratio rotation control input transmission wheel C1 is installed in sequence in accordance with the outer side keyway b15-19 (as shown in FIG. 7), and Medium speed ratio rotation control input transmission wheel C2, and high speed ratio rotation control input transmission wheel C3; the transmission wheel of each axis is installed with a limit sleeve 14 (as shown in Figure 4) to space the positional correlation of the positioning;

As shown in Figure 16, the low-speed ratio rotation input transmission wheel B (B11), the medium-speed ratio rotation input transmission wheel B (B21), and the high-speed ratio rotation input transmission wheel B (B31), the corresponding transmission wheel is installed on the rotary output shaft 2 On, equipped with bearing clutch 15;

Among them, the low speed ratio rotation control input transmission wheel C1, the medium speed ratio rotation control input transmission wheel C2, and the high speed ratio rotation control input transmission wheel C3 are provided with a bearing clutch 15 between the rotary transmission shaft 2-5;

As shown in Fig. 15, in the center shaft holes of the rotating output shaft 2 and the rotating speed-changing shaft 2-5, each having a different position and size, a follower wheel track 16-2 for locking and a follower wheel track 16-3 for disengagement are controlled. The shaft 16 (as shown in FIG. 9), the control inner shaft 16 has a coupling hole B16-1, and the control inner shaft moving groove a2-1 above each of the (rotation output shaft 2 and rotation shift shaft 2-5) passes ( As shown in FIG. 4) the interlocking pin 16-4 has an angle limitation relationship, so that the respective control inner shaft 16, the rotary output shaft 2 and the rotary speed change shaft 2-5, each of which has a synchronized rotation by the interlocking pin 16-4 Restrictive connection; through the combination of the linkage pin 16-4 and the output axial shift coupling disk 8-2 and the coupling hole A8-1 above the shift axial shift coupling disk 8-3, the output axial shift coupling disk 8- 2 with rotary output The shaft 2 is also equipped with a synchronous rotation restrictive coupling, and the same shifting axial shifting coupling disc 8-3 and the rotating shifting shaft 2-5 are also equipped with a synchronous rotating restrictive coupling; due to the rotating output shaft 2 and the rotating shifting shaft 2-5 The control internal shaft moving slot a2-1 above each is a long slot hole, so that the interlocking pin 16-4 can slide in the long slot hole, so the output axial shift coupling disk 8-2 and shift shaft The respective control inner shafts 16 of the variable speed coupling disk 8-3 can be slid within the range of the slot holes of the control inner shaft moving slot a2-1;

As shown in Fig. 15, the shifting handle 4 slides on the position restricting slot plate 5-1, and is connected with the long slot hole in the shifting shift rod 22 by the front axis 10 of the handle movement, and the fixed back axis 9 is used as the fixed rotation The shaft center, in which the shifting shift lever 22 fixes the center of the lever, pulls the shifting bidirectional ring 23 coaxial with the rotating output shaft 2 and the rotating shifting shaft 2-5, and outputs it on both sides through the cam follower 11 The axial shift coupling disk 8-2 and the shift axial shift coupling disk 8-3 make axial linkage traction, and the spring a6 exerts force on the rear side of the front axis 10 of the handle movement and the position limiting groove plate 5-1, The shifting lever 4 is caused to be attached to the front guide groove of the position restricting groove plate 5-1, and the displacement of the fixed value inching property due to the elastic force of the spring a6 is made, and the fixed value inching property is shifted. The size of the bit is converted into a follower wheel track 16-2 for locking above the inner shaft 16 and a follower wheel track 16-3 for disengagement, with respect to the rotary output shaft 2 and with respect to the rotary shift shaft 2-5 , The design value of the interference linkage opening and closing curve of the transmission wheels above each (see Figure 9 for the follower wheel track 16-2 for the phase-locking lock and the follower wheel track 16-3 for the disengagement). The fixed displacement of plate 5-1 means that the low to high speed transmission wheels above the rotating output shaft 2 and the rotating speed change shaft 2-5 are controlled Action points for control opening;

As shown in Fig. 15, suppose that the rotation input shaft 1 has the right rotation speed kinetic energy, the transmission wheels B11, B21, B31 installed in the keyway 1-1 have right rotation rotation kinetic energy; that is, the low-speed ratio rotation input transmission wheel B (B11) Linked low-speed ratio rotation control output transmission wheel B (B1), and medium-speed ratio rotation input transmission wheel B (B21), linked with medium-speed ratio rotation control output transmission wheel B (B2), and high-speed ratio rotation input transmission wheel B (B31) Interlocking high-speed ratio rotation control output transmission wheel B (B3), while rotating, driving low-speed ratio rotation control output transmission wheel B (B1) and medium-speed ratio rotation control output transmission wheel B (B2) and high-speed ratio rotation control output transmission wheel B(B3) also makes left-hand rotation synchronously;

(As shown in Fig. 15, first assume that the shift handle 4 is at the 0 position) At the same time, because the rotary input shaft 1 has the right rotation speed kinetic energy, through the speed-increasing transmission wheel combination 20, the speed is increased through the gear ratio, and the rotary shift shaft 2-5 It is the right rotation speed kinetic energy of 3.45 multiples of the rotation input shaft 1. At this time, the low speed ratio rotation control input transmission wheel C1 and the low speed ratio rotation output transmission wheel C11 are not linked, and the medium speed ratio rotation control input transmission wheel C2 and the medium speed The specific rotation output transmission wheel C21 is not linked, and the high-speed ratio rotation control input transmission wheel C3 and the high-speed ratio rotation output transmission wheel C31 are not linked;

As shown in Fig. 15, the shift position beside the shift handle 4 in front view B: and side view C: is marked as; (The following is the position description of 0, B1, B2, B3, C1, C2, C3, please refer to (Part numbers shown in Figure 15 and Figure 9):

The position marked as 0 in Fig. 15 means: according to Figs. 6 and 9, the rotating output shaft 2 does not move, because all the bearing clutches 15 in the transmission system have not been started, and the transmission wheels B1, B2, B3 and C1 , C2, C3 all the clutch lever follower 15-2 of the bearing clutch 15 are on the follower track 16-3 for disengagement, but the transmission wheels B11, B21, B31 and the corresponding B1, B2, B3 are Turning pattern

The position marked as B1 in Fig. 15 means: as shown in Figs. 6, 9, and 15, the shifting handle 4 is shifted to this position by a fixed distance, and the control input shaft 16 in the rotary input shaft 1 and the rotary shift shaft 2-5 is pulled Downwards, the clutch follower 15-2 of the bearing clutch 15 in the B1 area is activated by the locking follower track 16-2, prompting the start of interference linkage, and the low speed ratio rotation control output transmission wheel B (B1) starts to transmit the low speed ratio rotation Enter the low speed ratio of the rotational kinetic energy given by the transmission wheel B (B11), and transfer the rotational kinetic energy into the rotary output shaft 2 through the bearing clutch 15, at this time, the transmission wheel B1 rotates to do work, and the transmission wheels B21, B31 and the corresponding B2 and B3 are in continuous rotation form, and because the output shaft 2 starts to rotate, the transmission wheels C11, C21, and C31 are synchronously driven to rotate, and the transmission wheels C1, C2, and C3 are rotated in parallel;

The position marked as B2 in Fig. 15 means: according to Figs. 6, 9, and 15, the shifting handle 4 is shifted to this position by a fixed distance, and the inner shaft 16 is pulled to control the downward movement, and B2 is started by the locking follower track 16-2. The clutch lever of the zone-bearing clutch 15 follows the wheel 15-2 and begins to interfere with the linkage, so that the intermediate speed ratio rotation control output transmission wheel B (B2) starts to transmit the rotational kinetic energy given by the intermediate speed ratio rotation input transmission wheel B (B21) Medium speed ratio gives rotation In the process of output shaft 2, the rotational kinetic energy input by the original low-speed ratio rotation control output transmission wheel B (B1) does not need to be withdrawn. The medium-speed ratio rotation control output transmission wheel B (B2) increases the rotation speed of the rotary output shaft 2 from the original The low-speed rotation is changed to the medium-speed rotation output shaft 2, so the B1 zone bearing clutch 15 of the low-speed ratio rotation control output transmission wheel B (B1) makes a rotation overtaking action;

The position marked as B3 in Fig. 15 means: according to Figs. 6, 9, and 15, the shifting handle 4 is shifted to a fixed distance to this position, and the inner shaft 16 is pulled to control the downward movement again, and is started by the locking follower track 16-2 The clutch lever of the bearing clutch 15 in the B3 zone follows the wheel 15-2 and starts to interfere with the linkage, so that the high-speed ratio rotation control output transmission wheel B (B3) starts to transmit the high-speed rotation kinetic energy given by the high-speed rotation input transmission wheel B (B31) Specific rotational speed, the rotational kinetic energy input by the original low-speed ratio rotation control output transmission wheel B (B1) and the intermediate-speed ratio rotation control output transmission wheel B (B2) during the process can be exited, and the high-speed ratio rotation control output transmission wheel B (B3) The rotational speed of the rotating output shaft 2 has been increased, and the original intermediate speed has been changed to a high-speed rotating output shaft 2. Therefore, the bearing clutch 15 in the B2 zone of the intermediate speed ratio rotation control output transmission wheel B (B2) is also overtaken Actions.

The meaning of the position marked as C1 in Fig. 15 is: according to Figs. 6, 9, and 15, the shifting handle 4 is shifted to a fixed distance to this position, and the inner shaft 16 is pulled to control the downward movement again, and is started by the locking follower track 16-2 The clutch lever of the bearing clutch 15 in the C1 area follows the wheel 15-2 and starts to interfere with the linkage, so that the low-speed ratio rotation control input transmission wheel C1 starts to transmit the rotational kinetic energy speed given by the rotary transmission shaft 2-5, driving the low-speed ratio rotation output transmission Round C1 1, and directly increase the rotation speed of the rotating output shaft 2 during the process, the original low-speed ratio rotation control output transmission wheel B (B1) and the medium-speed ratio rotation control output transmission wheel B (B2) and the high-speed ratio rotation control output transmission wheel B (B3 ) The input rotational kinetic energy does not need to be withdrawn. The rotational kinetic energy rate given to the low-speed ratio rotary output transmission wheel C11 by the low-speed ratio rotation control input transmission wheel C1 of the rotary transmission shaft 2-5 also increases the rotational speed of the rotary output shaft 2, Therefore, the bearing clutch 15 in the B1, B2, and B3 zones driven by the rotary input shaft 1 also makes an overtaking action.

The supplementary data explanation is helpful for further understanding. The gear application example data shown in FIG. 15 is the speed-increasing transmission wheel combination 20>>((52 teeth/28 teeth)*(52 teeth/28 teeth))=3.45 Multiple, each transmission wheel >> (B1 50 teeth), (B2 40 teeth), (B3 30 teeth), (B11 30 teeth), (B21 40 teeth), (B31 50 teeth), (C1 30 teeth), ( C2 40 teeth), (C3 50 teeth), (C11 50 teeth), (C21 40 teeth), (C31 30 teeth); if the rotation input shaft 1 is set to 100 (rev/min), right-hand rotation will rotate the shift shaft 2 -5 is 345 (rev/min) right-hand rotation; when the transmission wheel is not started, the output shaft 2 is rotated 0 revolutions (per minute); when the transmission wheel B1 is started, the output shaft 2 is rotated 60 (revolutions per minute) Left-handed; drive shaft B2 rotates output shaft 2 to 100 (rev/min) left-handed; drive-wheel B3 rotates output shaft 2 to 166 (rev/min) left-handed; drive wheel C1 starts to rotate output shaft 2 to 207 (rev/min) left-handed; when the transmission wheel C2 starts, the output shaft 2 rotates 345 (rev/min) left-handed; when the transmission wheel C3 starts, the output shaft 2 rotates 575 (rev/min) left-handed;

The meaning of the position marked as C2 in Figure 15 is: according to Figure 6, 9, 15 The speed handle 4 is shifted by a fixed distance to this position, and the inner shaft 16 is pulled to control the downward movement again. The clutch follower 15-2 of the bearing clutch 15 in the C2 area is started by the locking follower track 16-2 and starts to interfere with the linkage, so that The intermediate speed ratio rotation control input transmission wheel C2 begins to transmit the rotational kinetic energy speed given by the rotary transmission shaft 2-5, driving the intermediate speed ratio rotation output transmission wheel C21, and directly linked to increase the rotational speed of the rotary output shaft 2, in the process of rotating input The B1, B2, B3, and C1 zone bearing clutches 15 of the rotating speed shaft 2-5 driven by the shaft 1 also make overrunning actions.

The position marked as C3 in Fig. 15 means: according to Figs. 6, 9, and 15, the shifting handle 4 is shifted to this position by a fixed distance, and the control inner shaft 16 is pulled down again to start the high-speed ratio rotation control input transmission wheel C3. Transmit the rotating kinetic energy speed given by the rotating speed change shaft 2-5, drive the high-speed rotating output transmission wheel C31, and directly increase the rotating speed of the rotating output shaft 2. During the process, the rotating input shaft 1 drives the B1 area, B2 area, The bearing clutch 15 in the zone B3, and the zones C1 and C2 of the rotary shift shaft 2-5 also make overrunning actions.

As described above, the transmission system device of the present invention refers to the feature that the high speed can directly surpass the low speed and return to the low speed gear when the speed is reduced, that is, it takes over the characteristics of the main transmission function (this is generally commercially available The one-way bearing has the function of overrunning clutch); the control mechanism transformed into multi-axis control and multi-speed ratio can be perfectly simple and easy to operate and control, and realize the economic and humanized high-efficiency mechanism-type effective practice.

More preferably, as shown in FIGS. It is used in variable speed systems of various sizes and types with high and low load design requirements of different mechanisms. It can be applied to smaller speed change devices or when the load capacity of the output shaft with higher load is required; the bearing type shown in Figure 8 The inner bearing ring ring 15-5 of the clutch 15 is combined with the rotary output shaft 2, and the inner bearing ring ring 15-5 is set as an integrated bearing inner ring ring 17-5, which becomes the integrated rotating shaft of the bearing inner ring ring 17, so that it has all the features of the bearing inner ring 15-5 and the rotating output shaft 2, including the steel ball and roller rolling outer edge c17-2, the clutch lever yield groove c17-4, interference engagement locking flange c17-6, steel ball limit arc ring c17-7 and central inner shaft hole c17-11 (as shown in Fig. 12), etc.; when sleeve bearing outer ring 15-12 or bearing outer ring ring integrated drive wheel 18 (such as Figure 13), the function is the same as when the bearing clutch 15 is sleeved on the rotating shaft; as shown in Figure 11F, it is a one-piece bearing inner ring ring full array 17-8 bearing inner ring ring integral rotating shaft 17, as shown in Figure 11F1 is an integrated type Bearing inner ring ring parts 17-9 of the bearing inner ring ring integral rotating shaft 17, of which the integrated bearing inner ring ring only configures part of the area, and the unconfigured area can be integrated into the bearing inner ring ring as required Any single or multiple area positions on the rotating shaft 17, the unconfigured area can be directly fixed by the keyway c17-10 for the transmission wheel, or it can be applied with a general one-way bearing sleeve, or the reverse configuration of the bearing clutch, as The design and matching scheme for the control of different coaxial rotation directions. The above changes can provide more specifications for the transmission system device. From the perspective view of FIG. 11G and FIG. 12, please understand the integral rotation shaft 17 of the bearing inner ring. The internal space, such as the structure of the center inner shaft hole c17-11 and the control inner shaft movement groove c17-1, and as shown in FIG. 11, all the genetic features (such as the part number control inner shaft movement groove a2-1 feature are turned into control Inner axis movement Features of slot c17-1, such as the bearing limit flange a2-3 is converted to the bearing limit flange c17-3, the clutch lever shift slot a2-4 and the clutch lever shift slot b15-4 are switched to the clutch lever Give way slot c17-4, center inner shaft hole a2-6 to center inner shaft hole c17-11, steel ball and roller rolling outer edge b15-3 to steel ball and roller rolling outer edge c17-2, interference engagement lock Flange b15-6 is converted into interference engagement locking flange c17-6, steel ball limit arc ring b15-13 is converted into steel ball limit arc ring c17-7, etc.), the rotary output shaft 2 is strengthened by the thickness of the inner wall of the shaft Make high-intensity applications;

It can be understood from the assembly part drawing of FIG. 11H and the perspective view of FIG. 111 that the operation of assembling other components of the bearing clutch 15 is the same as that described in [0019].

More preferably, please refer to Figures 8 and 13, where Figure 13M: is the bearing outer ring integral drive wheel 18, to combine the drive wheel 3 with the bearing outer ring 15-12, as shown in Figure 13L: bearing outer The ring-integrated transmission wheel 18, where the newly merged features are defined as: the rolling inner edge of the steel ball and roller d18-1 is the feature of the inner transmission side of the original transmission wheel and then reduced, and the steel ball and roller rolling inner edge b15-20 is converted Rolling inner edge d18-1 of steel ball and roller, contact with roller 15-8, with steel ball limit arc ring d18-2 and steel ball 15-10 to limit, the other side limit is locked by the limit of transmission wheel The cover 18-3 is implemented, and the bearing cage 15-7 and other components such as the roller 15-8 and the spring b15-9 and the steel ball 15-10 are installed on the inner side of the center circle, and the integral rotating shaft 17 with the inner ring of the bearing Or the bearing inner ring 15-5 is sleeved to realize all the functions when the bearing clutch 15 is sleeved to the drive wheel 3; as shown in Figure 14N: application example is a combined illustration, Figure 14O: is a three-dimensional combination illustration; is the outer bearing Front view and perspective view when the ring-integrated transmission wheel 18 and the bearing inner ring-integrated rotating shaft 17 are combined.

The application example is further illustrated, as shown in Figs. 9 and 10: the coupling hole B16-1 of the control inner shaft 16 is connected to the control inner shaft moving groove a2-1 of the rotary output shaft 2 (connected by the interlocking pin 16-4, from the perspective view of Fig. 4 and (Explosion diagram is understandable), so that the control inner shaft 16 and the rotary output shaft 2 have the ability to rotate synchronously. By controlling the inner shaft moving slot a2-1 and the key slot a2-2, the clutch lever on the rotary output shaft 2 is guaranteed to give way When the relative position of the groove a2-4 and the clutch lever shift groove b15-4 of the bearing clutch 15 is the same, and the clutch lever shift groove c17-4 of the bearing inner ring integral rotating shaft 17, the control When the relative positions of the inner shaft moving grooves a2-1 are consistent, the relative position on the inner shaft 16 can be controlled by using the follower track 16-3 to act as a limit to push the clutch lever 15- on the bearing cage 15-7 1 The clutch lever follower wheel 15-2; and the center of the coupling hole B16-1 of the inner shaft 16 is used as the design starting point to calculate the starting point and end point of the locking follower track 16-2 curve. The thickness of the transmission wheel can be easily calculated to a certain value, and the multi-axis multi-speed transmission system device to be designed and installed is controlled.

1‧‧‧rotation input shaft

1-1‧‧‧Keyway

12‧‧‧Rotation axis rotation direction sign

Claims (10)

A transmission system device mainly includes a rotating shaft, a transmission wheel (3), and a bearing clutch (15); the rotating shaft includes a rotating input shaft (1) and a rotating output shaft (2), and the main features include: A plurality of transmission wheels (3) are provided above each of the rotation input shaft (1) and the rotation output shaft (2); then between the rotation shaft and the transmission wheel (3) provided above it , Install a bearing clutch (15) as required to control the rotating shaft so that the transmission wheel (3) installed above the rotating input shaft or the rotating output shaft becomes free from the rotating shaft Rotating type, or meshing and locking with the rotating shaft to form an integrated linkage type. The transmission system device according to claim 1, wherein the main characteristics of the bearing clutch (15) include: It has a bearing inner ring (15-5) and a bearing outer ring (15-12), and a bearing cage (15-7) that can be controlled to rotate and shift by a relative angle to control whether the transmission wheel of the transmission system is input Or output rotational kinetic energy, which in turn controls the rotational speed of the rotary output shaft (2). The transmission system device according to claim 2, wherein the bearing clutch (15), the main features include: The bearing inner ring (15-5) is combined with the rotating input shaft (1) or the rotating output shaft (2), and the conversion is changed into a bearing inner ring ring integrated rotating shaft (17), the bearing inner ring The ring-integrated rotating shaft (17) may be in the form of an integral bearing inner ring ring full arrangement member (17-8) or an integral bearing inner ring ring partial arrangement member (17-9). The transmission system device according to claim 2, wherein the bearing clutch (15), the main features include: The bearing outer ring ring (15-12) described therein is merged with the transmission wheel (3), and the conversion device is changed into a bearing outer ring ring integrated transmission wheel (18). The transmission system device according to claim 2, claim 3, or claim 4, wherein the bearing clutch (15), the main features include: The control of the bearing cage (15-7) is to give a relative angle of rotation, and then the roller (15-8) in the bearing cage (15-7) and the bearing The interference engagement locking flange b (15-6) above the ring (15-5) contacts and interferes and the engagement lock becomes an integrated linkage state; and rotates a relative angle to retract the bearing cage (15-7), and The inner roller (15-8) is taken away from the contact area of the interference engagement locking flange b (15-6), and is converted into a free rotation state. The transmission system device according to claim 2, claim 3, or claim 4, wherein the bearing clutch (15), the main features include: The bearing inner ring (15-5) has a bevel tangent flange that interferes with the locking flange b (15-6) to generate a plurality of outer tangents from the outer periphery b (15-3) of the steel ball and roller rolling outer edge The inclined tangent flange becomes an interference engagement locking flange b (15-6), and the interference between the roller (15-8) on the bearing clutch (15) and the inclined tangent flange engages the locking flange b (15-6) Rotation away from the direction becomes free rotation without interference, and the inclined tangent flange interference engagement latching flange b (15-6) rotation in the close direction becomes interference engagement Locking linkage feature. The transmission system device according to claim 2, claim 3, or claim 4, wherein the bearing clutch (15) has a speed override function, and the main features include: The bearing inner ring (15-5) has interference engagement locking flange b (15-6), so that the spring b (15-9) in the bearing cage (15-7), for the roller (15-8) ) The elastic preload becomes the interference engagement locking force; due to the change in the relative speed of the bearing inner ring (15-5) and the bearing outer ring (15-12), the bearing outer ring (15-12) and the roller The rolling frictional force formed between (15-8) causes the roller (15-8) to move slightly away from the interference engagement blocking flange b (15-6) and causes the spring b (15-9) Produces a slight retraction against compressive force, so that the roller (15-8) loses the interference frictional force on the interference engagement locking flange b (15-6); promotes the bearing inner ring (15-5) and The bearing outer ring (15-12) has an overrunning function when the two have different rotational speeds. The transmission system device according to claim 1, wherein the bearing clutch (15) has a transmission wheel (3) installed above the rotary input shaft (1) or the rotary output shaft (2) In order to disengage from the rotation shaft and become a free-rotation type, or engage with the rotation shaft and become an integrated linkage type, the main features include: The center of the rotating shaft has a control inner shaft (16) with synchronous rotation speed, and the control inner shaft (16) has a follower wheel track (16-2) for locking and a follower wheel track (16-3) for disengagement. The transmission system device according to claim 8, wherein the center of the rotating shaft has a synchronous rotating speed control inner shaft (16), and the main features include: The control inner shaft (16) has a coupling hole B (16-1), which is connected with the rotating axial speed-changing coupling disk (8) or (output axial speed-changing coupling disk (8-2) and speed-changing axial speed-changing coupling disk (8-2) 8-3)) The coupling hole A (8-1) is connected in series by a linkage pin (16-4), and makes an axial movement in the control inner shaft moving groove a (2-1) and is connected with the rotating shaft According to this, the synchronous rotation is connected to control the transmission system. The transmission system device according to claim 1, claim 8, or claim 9, wherein the main characteristics of the bearing clutch (15) include: The central inner shaft hole a (2-6) of the rotating shaft has a control inner shaft (16) which can rotate synchronously and make axial displacement, through which the follower wheel track for locking on the control inner shaft (16) (16-2) and disengage the follower wheel track (16-3) to control the relative angular position of the bearing cage (15-7) in the bearing clutch (15) to complete the control of the transmission wheel type transmission system.

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