阅读说明：本技术 偏心平转无级变速器 (Eccentric flat-turning stepless speed changer ) 是由 周承岗 于 2018-07-13 设计创作，主要内容包括：偏心平转无级变速器,其特征在于以锥盘(19)和圆环(17)为摩擦副,有包括导轨(10、13)、滑座(12)和偏心轮(16)在内的平转机构控制其中一方绕着另一方的中轴平转,双方在施压装置的作用下接触进行摩擦传动。变速控制装置采用全自动或手动方式控制,通过调整偏心环的偏心程度来改变传动比,输出扭矩和转速负相关,具有恒功率特性,传动比可以趋向于无穷大。偏心平转无级变速器可以通过调压装置变换压力或者改变配重块位置来改变传动比和压力的对应关系,适应不同的载荷、道路状况或骑行习惯,此外还有临时手动增压、减压装置来防止特殊情况下打滑或者压力过大自动换挡困难。(The eccentric flat-turning stepless speed changer is characterized in that a conical disc (19) and a circular ring (17) are used as friction pairs, a flat-turning mechanism comprising guide rails (10, 13), a sliding seat (12) and an eccentric wheel (16) controls one of the two to rotate horizontally around the central axis of the other one, and the two sides are contacted under the action of a pressing device to carry out friction transmission. The speed change control device adopts full-automatic or manual control, changes the transmission ratio by adjusting the eccentricity degree of the eccentric ring, has negative correlation between the output torque and the rotating speed, has constant power characteristic, and can lead the transmission ratio to tend to infinity. The eccentric flat-turning continuously variable transmission can change the corresponding relation of transmission ratio and pressure by changing the pressure or the position of a balancing weight through the pressure regulating device, adapts to different loads, road conditions or riding habits, and also has temporary manual pressurization and pressure reducing devices to prevent the difficulty of slipping or automatic gear shifting with overlarge pressure under special conditions.)

1. The eccentric flat-turning stepless speed changer comprises a driving shaft (6), an output element, a friction pair, a speed change control device, a pressing device and a fixing device, and is characterized in that the friction pair comprises a conical disc (19) and a circular ring (17), an anti-rotation mechanism and an eccentric wheel (16) are arranged to control one of the two parts to rotate horizontally around the middle shaft of the other part, and the two parts are contacted under the action of the pressing device to carry out friction transmission; the transmission ratio is changed by the speed change control device automatically adjusting the eccentric degree of the eccentric wheel (16) through centrifugal action, or the speed change control device comprises a lead screw, a ball row, a deflector rod, a pull wire, a push rod, an air cylinder or a hydraulic cylinder which are controlled by the outside and can be used for adjusting the eccentric degree of the eccentric wheel (16).

2. The eccentric flat-turning continuously variable transmission according to claim 1, characterized in that the number of the pairs of the conical disks (19) and the circular rings (17) is at least two, and the centers of gravity thereof are uniformly distributed around the axis of the driving shaft (6) and have symmetrical motions so as to achieve dynamic balance.

3. The eccentric flat-turning continuously variable transmission according to claim 1 or 2, characterized in that a weight block (1) is mounted on the eccentric wheel (16) at the side far from the axis of the driving shaft (6), the relative distance between the gravity center position of the eccentric rotating assembly and the geometric center of the eccentric wheel (16) can be changed by adjusting the radial position of the weight block, so as to change the corresponding relation between the centrifugal force and the transmission ratio, and the gravity center of the weight block (1) is not coincident with the radial constraint force application point position of the driving shaft (6) on the eccentric wheel (16), is biased to the side where the conical disc (19) contacts the circular ring (17), so that the unbalanced state caused by the stress on one side of the conical disc (19) and the circular ring (17) can be reduced during the rotation.

4. The eccentric flat-turning continuously variable transmission according to claim 3, characterized in that a magnetic material is used to increase the pressure between the conical disk (19) and the annular ring (17).

5. The eccentric flat-turning continuously variable transmission according to claim 1, 2 or 4, wherein a pressure adjusting device is provided to adjust the pressing or tensioning degree of the pressing device to obtain different pressure schemes corresponding to the same transmission ratio.

6. The eccentric flat-turning continuously variable transmission according to claim 5, characterized by a temporary pressure boosting device or a temporary pressure relief device, which can be temporarily manually boosted to avoid slipping when an excessive load is encountered, or manually relieved when an automatic shift is difficult due to an excessive clamping force.

7. An eccentric rotory continuously variable transmission according to claim 1, 2, 4 or 6, wherein the shift control device includes gear locking means for locking the shift control device in a ratio position in which it cannot take a shifting action with a change in rotational speed.

8. The eccentric flat-turning continuously variable transmission according to claim 7, characterized in that the ring (17) or the conical disc (19) is of a split structure, and only the components of the friction transmission are made of friction materials.

Technical Field

The present invention provides a continuously variable transmission, particularly for use in a ride-on vehicle.

Background

The speed variator adopted by the current speed-variable bicycle mainly comprises a sprocket type outer speed variator and a star wheel type inner speed variator. The star wheel type internal speed changer is more and more popular due to the advantages of small occupied space, no pollution to clothes, no fear of being exposed to the sun and rain to drench silt and the like, but the defects of the step speed changer are still overcome, namely less selectable transmission and small speed change range are achieved. Only three transmission ratios are available for one star wheel combination, and the transmission ratios of adjacent gears cannot have too large fall, so that the speed change range can be limited within a common range suitable for common people to ride on common roads, the number of the star wheel combinations can be increased by increasing the selectable transmission ratio and expanding the speed change range, and the complexity and the cost of the whole system are too high due to the improvement of a speed change control mechanism, the maintenance is inconvenient, and the popularization is not facilitated.

Disclosure of Invention

The invention aims to provide a continuously variable transmission, in particular to a continuously variable transmission applied to riding vehicles, which improves the defects of less selectable transmission, small speed change range, complex structure, high manufacturing cost and the like of a star wheel type internal transmission. The invention comprises a driving shaft (6), an output element, a friction pair, a variable speed control device, a pressure applying device and a fixing device, and is characterized in that the friction pair is a conical disc (19) and a circular ring (17), an anti-rotation mechanism and an eccentric wheel (16) are arranged to control one of the two to rotate horizontally around the central axis of the other one, and the two parts are contacted under the action of the pressure applying device to carry out friction transmission; the transmission ratio is changed by the speed change control device automatically adjusting the eccentric degree of the eccentric wheel (16) through centrifugal action, or the speed change control device comprises a lead screw, a ball row, a deflector rod, a pull wire, a push rod, an air cylinder or a hydraulic cylinder which are controlled by the outside and can be used for adjusting the eccentric degree of the eccentric wheel (16).

The number of the pairs of the conical discs (19) and the circular rings (17) is at least two, and the centers of gravity of the conical discs and the circular rings are uniformly distributed around the axis of the driving shaft (6) and have symmetrical action, so that the dynamic balance is realized.

The eccentric wheel (16) of the invention is provided with the balancing weight (1) at the side far away from the axle center of the driving shaft (6), the relative distance between the overall gravity center position of the component which performs eccentric rotation and the geometric center of the eccentric wheel (16) can be changed by adjusting the radial position of the balancing weight, so that the corresponding relation between the centrifugal force and the transmission ratio is changed, moreover, the position of the gravity center of the balancing weight (1) in the axial direction is not coincident with the position of the radial constraint force application point of the driving shaft (6) to the eccentric wheel (16), and is deviated to the side where the conical disc (19) is contacted with the circular ring (17), and the unbalanced state caused by the single-side stress of the conical disc (19) and the circular ring (17) can be.

The invention uses magnetic material to increase the pressure between the conical disk (19) and the ring (17).

The invention has the pressure regulating device which can be used for regulating the compression or tension degree of the pressure applying device to obtain different pressure schemes corresponding to the same transmission ratio.

The invention is provided with a temporary pressure increasing device or a temporary pressure relief device, so that the pressure can be temporarily increased manually to avoid slipping when the load is overlarge, or the pressure can be manually relieved when the automatic gear shifting is difficult due to overlarge clamping force.

The gear locking device is arranged on the speed change control device, and the speed change control device can be locked at a certain transmission ratio position and cannot take a gear shifting action along with the change of the rotating speed.

The ring (17) or the conical disc (19) of the invention adopts a split structure, and only the friction transmission component is made of friction materials.

Drawings

FIG. 1 is a view of the radial structure of the integrated device;

FIG. 2 is a structural view in the direction A of a radial structural view of the overall device;

FIG. 3 is a view of the radial structure of the entire device showing the structure of the B-direction panning mechanism;

FIG. 4 is a block diagram of a built-in output reversing mechanism;

FIG. 5 is a schematic view of the geometric movement of the friction pair;

FIG. 6 is an axial view of the gear locking device;

FIG. 7 is a partial view of the gear locking arrangement from the C-direction axial view;

FIG. 8 is a structural view of an electric lead screw speed change control device;

fig. 9 is a structural view of the manual screw shift control device.

Detailed Description

Referring to fig. 1 and 2 (for convenience of explanation, this paragraph refers to fig. 1 and 2, and the supplementary presentation is provided in the sentence when more reference is needed), the friction pair of the present embodiment is a circular ring 17 and a conical disc 19, the circular ring 17 is rotatably connected with an eccentric 16, a sliding slot passing through the center of a circle is formed on the eccentric 16, a rectangular sliding block 15 can slide radially in the sliding slot and is limited in other directions, and the driving shaft 6 and the sliding block 15 are completely fixedly connected through a key 22 or can slide relatively in the axial range where the circular ring 17 and the conical disc 19 can keep contact and are fixed relatively in other directions. The eccentric 16 and the ring 17 can revolve with the driving shaft 6 as a whole, the initial position of the gravity center is not coincident with the revolution axis, the eccentric moves towards the direction of increasing eccentricity under the centrifugal action during rotation, a tension return spring 2 for applying the centripetal force to the eccentric 16 is arranged between the slide block 15 and the eccentric 16 in the eccentricity direction, and the return spring 2 can also be replaced by a compression spring arranged on the other side of the slide block 15. The magnitude of the centrifugal force exerted by the eccentric 16 in rotation in comparison with the centripetal force exerted by the return spring 2 determines the direction of deflection of the eccentric 16, thereby automatically changing the transmission ratio. In order to facilitate a user to operate the transmission according to his own habits or obtain manual fun, some embodiments may employ a lead screw and motor speed change control manner shown in fig. 8, in which a motor 32 is fixedly connected with one end of a chute of an eccentric wheel 16, the lead screw 31 penetrates through a slider 15 and a driving shaft 6, the other end is rotatably connected with the eccentric wheel 16, the other end is controlled by the motor 32, the eccentricity of the eccentric wheel 16 can be changed by forward rotation or reverse rotation of the motor 32, or a purely mechanical speed change control manner shown in fig. 9, in which the relative position of the slider 32 and the driving shaft 6 is fixed, a sliding rod 33 can slide along the radial direction of the slider 32 and is axially limited, two ends of the sliding rod 32 are respectively rotatably connected with a friction block 36, the friction block 36 is connected with the sliding; when no gear shifting is needed, the friction block 36 is in a position ready for gear shifting, the control wire 34 connected with the friction block 36 is released, and the friction block 36 is kept in a separated state from the rotating disc 37 under the action of the spring 35; when gear shifting is needed, the driving shaft 6 is rotated, the control wire 34 connected with the friction block 36 at one end is tightened, the controlled friction block 36 is in contact friction with one of the turntables 37 to rotate, the turntables 37 rotate to drive the lead screw 31 to rotate and move along the radial direction of the driving shaft to change the eccentricity degree of the eccentric wheel 16, meanwhile, the friction block 36 drives the sliding rod 33 to slide radially under the action of the radial force of the turntables 37 in contact with the friction block 36, the other friction block 36 is kept at the radial position of gear shifting preparation, and the control wire 34 is released to separate the friction block 36 after a target gear is reached; the other friction block 36 is operated in the same way when shifting in the opposite direction; the eccentricity of the eccentric 16 is set to a large enough area to make one friction pad 36 contact with only one of the turntables 37 during operation, so as to keep the radial positions of the friction pads 36 and the turntables 37 changing synchronously while the gear shifting is smoothly performed. In addition to the above list, other types of techniques may be used to adjust the eccentricity of the eccentric 16, including but not limited to bead-lining, wire-drawing, tie-rod, toggle, pneumatic, hydraulic, or combinations thereof. An anti-rotation mechanism is arranged to prevent the ring 17 from rotating, as shown in fig. 3, the slide rail 13 is fixed on the support 9, the slide rail 10 is vertically connected with the slide rail 13 and can slide along the slide rail 13, and the slide 12 is fixed on the slide rail 13 and can move in a two-dimensional space formed by the slide rail 10 and the slide rail 13 in a translation manner. Two points are selected on the end surface of the circular ring 17 and are respectively provided with a pin 11 to establish pluggable fixed connection with the sliding seat 12, so that the circular ring 17 can not rotate when revolving around the driving shaft 6 along with the eccentric wheel 16. In addition to the cross slide rail structure described above, the types of anti-rotation mechanisms that may be used may also include, but are not limited to, ball cross slide groove anti-rotation mechanisms, ball round groove anti-rotation mechanisms, ball bearing anti-rotation mechanisms, small crank anti-rotation mechanisms, cylindrical pin round hole anti-rotation mechanisms, or zero tooth difference anti-rotation mechanisms. The cone disc 19 is coaxially and rotatably connected with the driving shaft 6 through a bearing 21, and the cone disc 19 and the bearing 21 or the bearing 21 and the driving shaft 6 can axially slide. The back of the conical disk 19 is provided with a spring 20, but instead of this, a magnet, a pneumatic mechanism or a hydraulic mechanism may be used to push the conical disk 19 towards the ring 17 and keep them in a compressed state. In order to generate self-locking during pressing so that the circular ring 17 does not slide radially, the inclination angle between the generatrix of the conical disc 19 and the bottom surface of the cone is smaller than the maximum static friction angle required by the self-locking at the contact part of the conical disc 19 and the circular ring 17. The inner surface of the outer ring 14 is fixedly provided with an axial sliding groove formed by stop bars 18, a convex structure at the outer edge of the conical disc 19 is limited in the sliding groove and can slide along the sliding groove in the axial direction, and when the conical disc 19 rotates, the conical disc is output outwards through the outer ring 14. To change the rotation direction of the outer ring 14, a change gear set can be additionally arranged at the front end of the driving shaft 6 or between the driving shaft 6 and the eccentric wheel 16, or the structure shown in fig. 4 can be adopted, namely a conical disc 19 is connected with a gear ring 28 in a sliding mode through a sliding rod 23 and rotates synchronously in the circumferential direction, an idler wheel 27 is connected with a gear rim 25 in a rotating mode, the gear rim 25 is fixedly connected with the support 9, a gear ring 26 is fixed on the outer ring 14, and when the conical disc 19 rotates, the outer ring 14 can rotate in the opposite direction sequentially through the gear ring 28, the idler wheel 27 and the gear. The conical disk 19 may be an outer conical disk or an inner conical disk, and the relationship between the conical disk 19 and the circular ring 17 may be reversed, and the conical disk 19 is connected with the eccentric wheel 16 and rotates horizontally around the circular ring 17 as a driving part. Figure 5 illustrates the geometric motion law of the friction pair-when the ring 17 is rotated clockwise around the common axis Os, all particles on the device synchronously move in parallel clockwise along a circle with the center distance OsOd as a radius, the center Od, the mass point S1 and the mass point S2 respectively do circular motion along the trajectories Pd, P1 and P2, the mass point S1 at the vertex of the short axis is just in contact with the conical disk 19, when the rotating shaft moves clockwise, the conical disc 19 is driven to rotate anticlockwise, the mass point S1 is separated from the conical disc 19 after leaving the vertex position, at the moment, the next mass point S2 in the clockwise direction on the same circle reaches the short axis vertex and contacts the conical disk 19, so that the mass points on the same circle on the ring 17 contact and separate with the conical disk 19 one by one, the mass point S1 just returns to the position of the short axis vertex when the ring 17 rotates for one circle, and the circumferential travel of the same mass point on the contact radius of the conical disk 19 according to the track Ps is equal to the circumference of the circle with the center distance OsOd as the radius. The output torque of the conical disc 19 is inversely related to the rotating speed, and has a constant power characteristic. The transmission ratio i =2R/(R-R) of the ring 17 to the conical disc 19, i tends to be infinite when R and R are infinitely close, i is infinitely close to zero, i =1 when R =3R, and i =0.6 when R =4R, the size of the friction pair corresponding to the speed change range is acceptable for riding vehicles such as bicycles and electric bicycles, and the minimum speed change ratio is limited to be above 0.6 by referring to three speed ratios 1.4, 1 and 0.7 commonly used for the inner three speeds, and the maximum speed change ratio is far enough from infinity to be safe, i.e. a minimum center distance is set to prevent the torque overload from damaging the machine members.

Referring to fig. 1, in order to achieve the rotational balance, at least two pairs of conical disks 19 and rings 17 are provided, and the centers of gravity of the conical disks and the rings are uniformly distributed around the axis of the driving shaft 6 and have symmetrical motions.

Referring to fig. 1, a balancing weight 1 is installed on one side, far away from the axis of a driving shaft 6, of an eccentric wheel 16, different installation positions are preset through a theoretical calculation or test method, and are marked with scales, then the balancing weight is fixedly installed through screws, the balancing weight is detached to be installed at a place to be changed when the balancing weight needs to be adjusted, a screw rod can be installed, and the screw rod can be rotated when the position needs to be adjusted. The relative distance between the overall gravity center position of the assembly which does eccentric rotation and the geometric center of the eccentric wheel 16 can be changed by adjusting the radial position of the balancing weight 1, so that the corresponding relation between centrifugal force and transmission ratio is changed, moreover, the gravity center of the balancing weight 1 does not coincide with the radial constraint force application point position of the driving shaft 6 on the eccentric wheel 16 at the axial position, the balancing weight is deviated to one side of the conical disc 19 which is contacted with the circular ring 17, the twisting action of the centrifugal force on the eccentric wheel 16 during rotation is opposite to the effect generated by the conical disc 19 applying pressure on the single side of the circular ring 17, and the unbalanced state can be relieved.

Referring to fig. 1, in the case of limited space, the pressure provided by the spring 20 due to the size may be insufficient, and in order to obtain more pressure, the magnetic material is fixedly installed on the eccentric wheel 16 or the ring 17, and the conical disc 19 contains the material capable of being attracted by the magnetic material, so that the magnetic material can take the task of improving the stress condition on one side like the counterweight block 1 while obtaining more pressure through attraction.

As shown in figure 1, the side of the eccentric wheel 16 is provided with a conical flange 5, the inner side of the pressure regulating knob 7 is in threaded connection with the driving shaft 6, the outer side is rotatably connected with the support 9 through a bearing 8, one end of the pressure regulating knob is exposed out of the outer side of the support 9, and the other end of the pressure regulating knob is in contact with the outer end surface of the conical flange 5 at the inner side of the support 9. When the pressure regulating knob 7 is screwed inwards, the conical flange 5, the eccentric wheel 16, the ring 17 and the conical disc 19 are sequentially pushed to move inwards, the spring 20 is compressed, so that the returned pressure is higher, and when the pressure regulating knob 7 is screwed outwards, the pressure provided by the spring 20 is reduced, so that the pressure regulating knob 7 can obtain different pressures corresponding to the same transmission ratio at different positions, and different riding habits, road conditions or load conditions are adapted.

Referring to fig. 1, a pull ring 4 is sleeved on the outer side of a conical flange 5, one end of a pull wire 3 is connected with the pull ring 4, and the other end extends to the outside through a hole on a support 9. When a friction pair slips when the load is too large, a user pulls the pull ring 4 through the pull wire 3 to extrude the conical surface of the conical flange 5 in the axial direction, the axial component force of the pull ring pushes the conical flange 5, the eccentric wheel 16, the circular ring 17 and the conical disc 19 to move inwards in sequence, the spring 20 is compressed to obtain higher pressure, and after the external pulling force is removed, the pull ring 4 is pushed back to the original position by the conical surface of the conical flange 5. The pull ring 4 may be replaced by other types of devices including, but not limited to, a lever, a screw press, a pneumatic ram, a hydraulic ram, or an electric ram. The supercharging device can also adopt a bidirectional adjusting structure and has a pressure relief function, so that pressure can be manually relieved when automatic gear shifting is difficult due to overlarge clamping force.

Referring to fig. 6 and its C-direction view fig. 7, a V-shaped groove is provided on the side of the sliding block 15 in sliding contact with the eccentric wheel 16, a wedge 29 with gradually changing axial dimension is provided in the groove, one end is large and the other end is small, the size of the small end does not affect the sliding between the sliding block 15 and the eccentric wheel 16, but when the front large end is squeezed into the V-shaped groove, the size of the middle part is enough to wedge the sliding block 15 and the eccentric wheel 16, so that the eccentric position of the eccentric wheel 16 cannot be automatically adjusted when the rotation speed is changed. The wedge block 29 is fixedly connected with a push-pull rod 30, the sliding block 15 and the eccentric wheel 16 are wedged and debugged through the axial movement of the push-pull rod 30, one end of the push-pull rod 30 extends out, the axial movement of the push-pull rod 30 can be directly controlled by the outside, and the control can also be performed through a lever, a wire pulling system, a pneumatic device, a hydraulic device or an electric device.

Referring to fig. 1, in order to facilitate the use of special materials and special manufacturing processes, the ring 17 or the conical disk 19 is of a split structure, and only the friction transmission components are made of friction materials.

The pneumatic, hydraulic, electrohydraulic, photoelectric or microelectronic automatic or intelligent system is used for speed change control, pressure application, overload prevention, operation monitoring or fault diagnosis and alarm.