CN110778684A

CN110778684A - Reducing chain wheel and reducing chain wheel transmission

Info

Publication number: CN110778684A
Application number: CN201911253186.0A
Authority: CN
Inventors: 郑福建
Original assignee: Individual
Current assignee: Individual
Priority date: 2019-12-10
Filing date: 2019-12-10
Publication date: 2020-02-11
Also published as: WO2021115024A1; CN110985636A

Abstract

The invention discloses a reducing chain wheel for mechanical variable speed transmission and a reducing chain wheel transmission. The reducing chain wheel mainly comprises two conical discs which are coaxially opposite, a chain between the conical discs and a chain coiling shaft in a central through hole of the conical discs; the conical surfaces of the two conical disks are opposite, and a sliding groove is arranged in the direction of a generatrix of the conical surfaces; the chain is arranged on the chain rolling shaft; the inner end of the chain is connected to the chain winding shaft, the outer end of the chain extends from the space between the two conical disks from inside to outside, and the extended part is circumferentially surrounded on the two conical surfaces to form a chain ring. The variable diameter chain wheel has the advantages that: the diameter and the circumference of the chain ring of the reducing chain wheel can be changed, so that the effect of the reducing chain wheel as a mechanical transmission part is the same as the variable speed transmission effect achieved by an ideal reducing gear. The variable diameter chain wheel transmission mainly comprises a variable diameter chain wheel and a transmission piece. Its advantage does: when the transmission is used as an automobile transmission, the transmission has the advantages of high manual transmission efficiency and large torque, and also has the advantages of continuous and smooth speed change and small size of a mechanical Continuously Variable Transmission (CVT).

Description

Reducing chain wheel and reducing chain wheel transmission

Technical Field

The invention relates to a reducing chain wheel and a reducing chain wheel transmission, in particular to a reducing chain wheel and a reducing chain wheel transmission for mechanical variable speed transmission.

Background

In the field of mechanical transmission, the most commonly used transmission parts for transmitting the rotating speed of one rotating part to other rotating parts efficiently with high torque are gears, chain wheels, chains and the like, and the transmission modes are meshing transmission between the gears and chain transmission between the chain wheels through the chains respectively. The most important and common transmission field requiring a specific speed change is the transmission on a vehicle. Conventional automotive transmissions are classified into manual transmissions and automatic transmissions. The automatic transmissions are roughly hydraulic automatic transmissions, electric control mechanical automatic transmissions, double-clutch automatic transmissions and mechanical stepless automatic transmissions. Conventional automotive transmissions suffer from a number of significant disadvantages due to the limitations of the diameter of conventional gears or sprockets which cannot be changed. The manual transmission has the defects of inconvenient operation, few gears and strong and unsmooth pause and contusion during gear shifting; the hydraulic automatic transmission has the disadvantages of complex structure, high cost, too small torque and low transmission efficiency (because of the low transmission efficiency of the hydraulic torque converter); the disadvantage of the automatic transmission of the electric control machine is that the gear shifting has a pause feeling (because the nature of the transmission mode is the same as the principle of a manual transmission) and the requirement on an electric control system is very high; the double-clutch automatic transmission has the disadvantages of large volume, few gears, jerky feeling (because the nature of a transmission mode is the same as the principle of a manual transmission) and high failure rate; the mechanical stepless automatic transmission has the defects of small load, easy slipping, high manufacturing cost of a chain and the like because the smooth surface clamping steel belt of the opposite conical disc is adopted to transmit by using the friction force between the steel belt and the conical surface. Besides, the traditional transmission needs a plurality of clutches for matching, and the clutch is easy to slip and burn during working. For the above reasons, for many years, people have been trying to find a way to design an ideal reducing gear with a diameter and number of teeth that can be changed according to various speed changing requirements.

Disclosure of Invention

The invention provides a variable diameter chain wheel with diameter and circumference capable of changing according to requirements, which is characterized in that the diameter and circumference of a chain ring contained in the variable diameter chain wheel can be changed linearly. When the gear is used as a mechanical transmission part, the transmission effect of the gear is the same as that of an ideal reducing gear in human conception.

In order to realize the characteristics, the technical scheme of the variable-diameter chain wheel disclosed by the invention is as follows:

a variable diameter chain wheel mainly comprises two conical disks which are coaxially opposite, a chain between the conical disks and a chain coiling shaft in a central through hole of the conical disks; the conical surfaces of the two conical disks are opposite, and a sliding groove is arranged in the direction of a generatrix of the conical surfaces; the chain is arranged on the chain rolling shaft, the inner end of the chain is connected to the chain rolling shaft, the outer end of the chain extends from the space between the two conical disks from inside to outside, and the extended part is circumferentially surrounded on the two conical surfaces to form a chain ring; the roller chain shaft can rotate relative to the conical discs, and at least one of the two conical discs can axially move relative to the roller chain shaft. The whole conical disc is in a circular truncated cone shape, a top shape, a conical shape or other similar shape structures with a central through hole.

The rotation of the chain winding shaft can wind or release the chain connected to the chain winding shaft; when the conical discs move outwards in the axial direction to enable the two conical discs to be away from each other, the chain winding shaft rotates for winding the chain; when the conical discs move axially inwards to enable the two conical discs to approach each other, the chain rolling shaft rotates to release the chain.

A notch is formed in the inner end of the conical disc, the notch penetrates through the central through hole and the conical surface of the conical disc, and the notch is adjacent to the sliding groove; the two sides of the chain section extending from the inside to the outside between the two conical discs pass through the notch. The outer end of the chain ring is mounted in the chute in a direct or indirect manner.

As an alternative, a coil spring is provided between the link shaft and the conical disk, which coil spring exerts a winding force of the winding chain on the link shaft.

The chain can be a roller chain, a tooth-shaped chain, or other belt-shaped bodies or chain-shaped bodies which can be wound and adapted.

The sliding block is arranged in the sliding groove and matched with the sliding groove, the sliding block is clamped in the sliding groove and can slide in the sliding groove, and the outer end of the chain ring is directly or indirectly connected to the sliding block.

Preferably, a central shaft is provided at one end or both ends of the spool, and the spool is axially connected to the central shaft directly or indirectly. A chain drum is arranged between the chain rolling shaft and the conical disc, and the chain drum is sleeved on the periphery of the chain rolling shaft and can rotate relatively to the chain rolling shaft; the conical disc is sleeved on the periphery of the chain drum, and a transmission shaft is directly or indirectly arranged at one end or two ends of the chain drum. The chain drum is of a cylindrical structure with an opening in the side wall. The transmission shaft is directly or indirectly axially connected with the chain drum. The inner wall structure of the conical disc is matched with the peripheral structure of the chain drum; the two conical discs can only axially slide on the periphery of the chain drum but cannot rotate.

Preferably, the inner wall of the conical disc is provided with a bump, and the outer wall of the chain drum is provided with a clamping groove; the lug is matched with the clamping groove and can axially slide relatively. Because the lug and the clamping groove are matched, the conical disc can only axially slide on the periphery of the chain drum but cannot rotate. And the outer end of at least one of the two conical disks is provided with a push-pull device which can apply axial push-pull force to the conical disks.

Preferably, the transmission shaft has an overall cylindrical structure.

Preferably, the transmission shaft is sleeved on the periphery of the central shaft and can rotate relatively between the central shaft and the transmission shaft; the central shaft is provided with at least one spiral slot or straight slot; the shaft wall of the transmission shaft is provided with at least one straight slot hole or spiral slot hole; and a push rod or a ball is arranged in the straight slot hole or the spiral slot hole. The push rod is of a rod-shaped structure.

Preferably, a push rod or a ball is arranged between the transmission shaft and the central shaft, and the push rod (or the ball) is simultaneously positioned in a straight slot (or a spiral slot) on the transmission shaft and a spiral slot (or a straight slot) on the central shaft.

Preferably, the straight slot hole (or the spiral slot hole) penetrates the transmission shaft from inside to outside, a sliding sleeve is arranged on the periphery of the transmission shaft, the sliding sleeve can slide on the periphery of the transmission shaft, and the end of the push rod is arranged on the sliding sleeve. The push rod can move in the spiral groove hole along the spiral direction.

When the sliding sleeve drives the push rod to slide on the transmission shaft, the push rod performs axial spiral movement in the spiral groove hole, and the central shaft rotates relative to the transmission shaft due to spiral torsional force generated by the spiral movement of the push rod.

As an alternative, in order to reduce the number of turns and the length of the helical slot, a speed change device is provided between the chainring axle and the central axle. The speed changing device enables the rotation angle of the central shaft to be smaller than the rotation angle of the roller chain shaft in the same time. If no speed change device is provided between the central shaft and the spool shaft but the central shaft and the spool shaft are directly connected, the angles of rotation of the central shaft and the spool shaft are equal during winding (or releasing) the chain from the maximum release state (or winding state) to the maximum winding state (or release state). If a speed change device is arranged between the central shaft and the winding chain shaft, so that the rotation angle of the central shaft is smaller than that of the winding chain shaft in the same time, the rotation angle of the central shaft in the process of winding (or releasing) the chain from the maximum releasing state (or winding state) to the maximum winding state (or releasing state) is smaller than that of the winding chain shaft, and the required number of turns of the spiral groove holes is also reduced to the same extent. Since the length of the spiral groove is shorter as the number of turns of the spiral groove is smaller under the condition that the pitch and the diameter of the spiral groove are not changed, the number of turns and the length of the spiral groove on the central shaft can be reduced after a speed changing device is arranged between the central shaft and the chain winding shaft, and the length of the whole central shaft and the transmission shaft can be further reduced.

As an alternative, the reduction device is a planetary gear mechanism. The sun gear of the planetary gear mechanism is connected with the chain winding shaft, the planetary gear is connected with the central shaft, and the gear ring is connected with the conical disc or the chain drum or the transmission shaft.

As an alternative, the roller chain shaft and the central shaft may also be provided as a unitary structure; the chain drum and the transmission shaft can also be designed as an integral structure.

As an alternative, a coil spring is arranged between the transmission shaft and the central shaft, and the coil spring applies a winding force to the central shaft to drive the chain winding shaft to wind the chain.

The variable diameter chain wheel has the advantages that: when the angular speed of the chain ring rotation is constant, the push-pull device is operated to move the conical disc and synchronously rotate the chain winding shaft, so that the diameter and the circumference of the chain ring can be synchronously changed, and the linear speed of the chain ring rotation can be changed. Because the reducing chain wheel is directly meshed with an external gear or a transmission belt for transmission by a chain ring when being used as a mechanical transmission part, the transmission effect of the reducing chain wheel when being used as the mechanical transmission part in the field of mechanical transmission is the same as the variable transmission effect achieved by an ideal reducing gear with the assumed diameter and tooth number which can be synchronously changed according to the requirement.

The invention also discloses a variable-diameter chain wheel transmission, which comprises the variable-diameter chain wheel and a transmission piece, wherein the transmission piece is arranged on one side of the variable-diameter chain wheel; the transmission part is a gear or a transmission belt matched with the chain ring of the reducing chain wheel.

As an example, the gear consists of a wheel and a tooth. The gear teeth of the gear are of a movable tooth structure; a plurality of tooth holes are formed in the periphery of the wheel disc, and the wheel teeth are installed in the tooth holes; the outer end structure of the gear teeth can be meshed with the chain links of the chain ring; a spring is arranged in the wheel disc, the upper end of the spring is abutted against the bottom of the wheel teeth, and the lower end of the spring is abutted against the inner wall of the wheel disc; the gear teeth can slide in the gear holes. The gear is arranged on a gear shaft; gear carriers are respectively arranged at two ends of the gear shaft; the gear rack is of a rectangular frame-shaped structure; the gear rack is internally provided with a shaft sleeve, and two ends of the gear shaft are arranged on the shaft sleeve. A spring is arranged between the shaft sleeve and the gear rack; the pressing of the spring to the shaft sleeve enables the gear to be abutted to the chain ring. The shaft sleeves can slide in the gear frame in a left-right parallel mode.

Preferably, the chain is a roller chain. The gear is a double-row gear or a multi-row gear. The gear and the chain ring are in external tangent engagement with each other.

As an embodiment, in order to increase the speed change range, the variable diameter chain wheels are provided with a left set and a right set in parallel, the transmission part is arranged between the left set and the right set of the variable diameter chain wheels, and the transmission part is in matched transmission contact with chain rings on the two variable diameter chain wheels.

The variable diameter chain wheel transmission has the beneficial effects that: the speed at which the chain loop is output is also linearly variable because the diameter of the chain loop can be linearly varied; when in transmission, the transmission fit between the chain ring and the gear is similar to that between the traditional rigid gear and is rigid and continuous, so the transmission efficiency is high and the torque is large. Therefore, when the variable-diameter chain wheel transmission is used as a transmission of an automobile, the variable-diameter chain wheel transmission has the advantages of high transmission efficiency and large torque of a traditional manual gear and has the advantages of continuous and smooth speed change and small size of a mechanical Continuously Variable Transmission (CVT).

Drawings

Fig. 1 is a diagram illustrating the working state of two conical disks, a chain, a sliding block, a chain drum, a transmission shaft, a central shaft, a push rod, a sliding sleeve, a push-pull device, and the like, when the two conical disks are away from each other according to an embodiment of the present invention.

Fig. 2 is a left side view of the drawing.

Fig. 3 is a schematic structural diagram of a conical disc according to a first embodiment of the present invention.

Fig. 4 is a top view of fig. 3.

Fig. 5 is a schematic perspective view of fig. 3.

Fig. 6 is a schematic structural diagram of the cooperation between the roller chain shaft and the central shaft in the first embodiment of the invention.

Fig. 7 is a perspective view illustrating the matching of the roller chain shaft, the central shaft and the push rod in the first embodiment of the invention.

Fig. 8 is a schematic perspective view of a chain drum and a transmission shaft according to a first embodiment of the present invention.

Fig. 9 is a perspective view illustrating the engagement of the chain drum, the transmission shaft, the chain winding shaft, the central shaft and the push rod according to the first embodiment of the present invention.

Fig. 10 is a schematic view showing the engagement of the two conical disks with the chain drum, the transmission shaft, the chain winding shaft, the central shaft, the push rod, and the like when the two conical disks are away from each other in the first embodiment of the present invention.

Fig. 11 is a perspective view of fig. 10.

Fig. 12 is a schematic view showing the cooperation between the two conical disks and the chain ring, the sliding block, the chain drum, the transmission shaft, the chain winding shaft, the central shaft, the push rod, the sliding sleeve and the like when the two conical disks are away from each other in the first embodiment of the invention.

Fig. 13 is a perspective view of fig. 12.

Fig. 14 is a sectional view a-a of fig. 12.

Fig. 15 is a schematic view showing the engagement between the two conical disks and the chain drum, the transmission shaft, the chain winding shaft, the central shaft, the push rod, the sliding sleeve, etc. when the two conical disks are close to each other according to the first embodiment of the present invention.

Fig. 16 is a schematic view showing the engagement between the two conical disks and the chain ring, the sliding block, the chain drum, the transmission shaft, the chain winding shaft, the central shaft, the push rod, the sliding sleeve, etc. when the two conical disks are close to each other in the first embodiment of the present invention.

Fig. 17 is a sectional view taken along line B-B of fig. 16.

Fig. 18 is a diagram illustrating an operation state of two conical disks in a state of being close to each other according to the first embodiment of the present invention.

FIG. 19 is a schematic diagram of the engagement between the variable diameter sprocket and the gear when the two conical disks are away from each other according to the second embodiment of the present invention.

Fig. 20 is a perspective view of fig. 19.

Fig. 21 is a schematic view of the engagement between the variable diameter sprocket and the gear when the two conical disks are close to each other according to the second embodiment of the present invention.

FIG. 22 is an enlarged view in partial section of the structure of the gears and the intermeshing of the gears and chain rings.

Fig. 23 is a schematic diagram of a third embodiment of the present invention, in which when two tapered disks of the left reducing chain wheel are away from each other, two tapered disks of the right reducing chain wheel are close to each other, and the left reducing chain wheel and the right reducing chain wheel are engaged with a gear.

Fig. 24 is a schematic view of a third embodiment of the present invention, in which when two tapered disks of the left reducing chain wheel are in a state of being close to each other, two tapered disks of the right reducing chain wheel are in a state of being away from each other, and the left reducing chain wheel, the right reducing chain wheel, and a gear are engaged with each other.

Fig. 25 is a schematic view of the matching between the left and right variable diameter chain wheels and the transmission belt in the fourth embodiment of the invention.

Detailed Description

Example one

The following examples are used to further illustrate the variable diameter sprocket disclosed in the present invention:

as shown in fig. 1 to 18, the variable diameter chain wheel mainly comprises two conical disks 1 which are coaxially opposite, a chain 4 between the conical disks 1, and a chain winding shaft 21 in a central through hole of the conical disks 1.

As shown in fig. 3 to 5, the whole conical disc 1 is in a circular truncated cone shape, a top-shaped or a conical shape with a central through hole; a sliding groove 50 is arranged in the generatrix direction of the conical surface of the conical disc 1; a notch 10 is arranged at the inner end of the conical disc 1; the notch 10 penetrates through the central through hole and the conical surface of the conical disc 1; the notch 10 is located adjacent to the chute 50. As shown in fig. 1, 2, 10 to 13, 15, 16 and 18, the conical disk 1 is provided with two coaxially opposed; the sliding grooves 50 on the two conical disks 1 face each other; the notches 10 of the two conical discs 1 face each other. As shown in fig. 1, 2, 6, 7 and 10 to 18, a roller chain shaft 21 is arranged in the central through hole of the two conical disks 1; the chain 4 is arranged on the chain winding shaft 21; the inner end of the chain 4 is hinged on the chain winding shaft 21; the outer end of the chain 4 extends from the inside to the outside between the two conical discs 1 and surrounds the extended part on the two conical surfaces to form a chain ring 41, and the outer end of the chain ring 41 is directly or indirectly connected in the two sliding grooves 50. As shown in fig. 14 and 17, the spool 21 can rotate relative to the two conical disks 1; the rotation of the winding chain shaft 21 enables winding or releasing of the chain 4 articulated thereto. As shown in fig. 10 to 18, at least one of the two conical disks 1 is axially movable relative to the spool 21.

As shown in fig. 1 to 18, the variable diameter chain wheel further comprises a central shaft 2, a transmission shaft 3, a chain drum 33, a sliding block 5, a sliding sleeve 6, a push rod 7, a push-pull device 8 and the like.

As shown in fig. 3 to 5, the notch 10 and the chute 50 are adjacent to each other on the conical disk 1 and communicate with each other. The two sides of the chain section extending from inside to outside between the conical discs 1 pass through the gap 10.

As shown in fig. 22, the chain 4 is a roller chain.

As shown in fig. 1, 12, 13, 14, and 16 to 18, the sliding groove 50 is provided therein with a sliding block 5 adapted thereto; the sliding block 5 is clamped in the sliding groove 50, and the sliding block 5 can slide in the sliding groove 50; the end of the chain loop 41 is directly or indirectly connected to the sliding block 5.

As shown in fig. 1, 6, 7 and 9 to 13, in order to facilitate the rotation of the zipper shaft 21 relative to the two conical disks 1, a central shaft 2 is provided at one end or both ends of the zipper shaft 21; the chainring spindle 21 is axially connected to the central spindle 2.

As shown in fig. 1, 2, 8 to 11, 14 and 17, in order to facilitate handling of the movement of the two conical disks 1 relative to the spool 21, a chain drum 33 is provided between the spool 21 and the two conical disks 1; the chain drum 33 is a cylindrical structure with an opening 40 on the side wall; the chain drum 33 is sleeved on the periphery of the chain winding shaft 21, and the two conical discs 1 are sleeved on the periphery of the chain drum 33; one end or two ends of the chain drum 33 are provided with transmission shafts 3; the transmission shaft 3 is of a cylindrical structure; the transmission shaft 3 is axially connected with the chain drum 33; the drive shaft 33 is fitted around the outer periphery of the central shaft 2. The inner wall structure of the conical disc 1 is matched with the outer periphery structure of the chain drum 33.

As shown in fig. 8, 9, 11, 14 and 17, in order to make the inner wall structure of the conical disc 1 fit with the outer peripheral structure of the chain drum 33, a protrusion 11 is provided on the inner wall of the conical disc 1, a slot 300 is provided on the outer wall of the chain drum 33, and the protrusion 11 fits with the slot 300 and can slide axially. Because the projection 11 and the slot 300 are matched, the conical disc 1 can only axially slide on the periphery of the transmission shaft 3 and can not rotate.

As shown in fig. 1, 2 and 18, at least one of the conical disks 1 is provided at its outer end with a push-pull 8 in order to be able to manipulate the conical disk 1 for axial sliding on the chain drum 33. The working principle of the push-pull device 8 is the mechanical shifting fork push-pull principle in the prior art, and is not described in detail herein.

In order to synchronously control the winding or releasing of the chain 4 by the chain winding shaft 21 while the push-pull device 8 pushes and pulls the conical disc 1, as shown in fig. 6 to 18, two centrosymmetric straight slot holes 30 are axially arranged on the shaft wall of the transmission shaft 3, and the straight slot holes 30 are in a straight strip-shaped hole structure; the straight groove hole 30 penetrates the inside and outside of the transmission shaft 3. The periphery of transmission shaft 3 is equipped with sliding sleeve 6, and sliding sleeve 6 can slide in the periphery of transmission shaft 3. The sliding sleeve 6 is provided with a push rod jack. The central shaft 2 is provided with two spiral groove holes 20; the two spiral groove holes 20 are circumferentially and uniformly distributed on the central shaft 2 and have consistent spiral directions; the two spiral groove holes 20 are provided with straight rod-shaped push rods 7, the push rods 7 are radially inserted into the spiral groove holes 20, and the push rods 7 can axially move along the spiral groove holes 20 in the spiral groove holes 20. The shape of the chainreel 21 is adapted to the mounting and winding of the chain 4. The two ends of the push rod 7 pass through the straight slotted holes 30 and are arranged in the push rod jacks on the sliding sleeve 6. When the sliding sleeve 6 slides on the transmission shaft, the sliding sleeve 6 drives the push rod 7 to move linearly along the hole wall in the straight slot 30 relative to the transmission shaft 3, and the push rod 7 moves spirally along the slot wall of the spiral slot 20 in the spiral slot 20, so that the push rod 7 twists the central shaft 2 to rotate relative to the transmission shaft 3 when the sliding sleeve 6 slides on the transmission shaft in a directional manner. The rotation of the central shaft 2 drives the winding shaft 21 to wind or release the rotation of the chain 4.

The diameter and the perimeter of the chain ring of the reducing chain wheel are changed as follows:

as shown in fig. 1, 2, 14, 17 and 18, since the width of the chain ring 41 and the length of the outer end of the chain ring 41 are not changed, the two sliding blocks 5 in the sliding slots 50 slide outwards simultaneously under the compression of the two sliding slots 50 while the two tapered discs 1 are pushed inwards by the push-pull device 8 to gradually draw close to each other, and simultaneously the whole chain ring 41 slides outwards synchronously along the tapered surfaces due to the compression of the two tapered surfaces on the two sides, and the force of the chain ring 41 sliding outwards along the tapered surfaces applies an outwards releasing pulling force to the chain 4 wound on the winding shaft 21; meanwhile, the sliding sleeve 6 is synchronously slid downwards on the transmission shaft 3 in the process that the push-pull device 8 pushes the two conical discs 1 inwards to gradually draw close to each other, and the central shaft 2 drives the chain rolling shaft 21 to rotate for releasing the chain 4 by the synchronous sliding of the sliding sleeve 6; under the synchronous action of the chain releasing rotation of the chain winding shaft 21 and the pulling force of the chain ring 41 on the chain 4, the chain length wound on the chain winding shaft 21 is gradually released and reduced, and the chain length and the diameter of the chain ring 41 are gradually increased. If the angular velocity of the outside world input through the center shaft 3 and transmitted to the rotation of the chain ring 41 is not changed in this process, the linear velocity of the rotation of the chain ring 41 becomes gradually larger due to the gradually larger diameter and circumference of the chain ring 41. On the contrary, in the process that the push-pull device 8 pulls the two conical disks 1 outwards to gradually move away from each other, the two sliding blocks 5 in the sliding grooves 50 slide inwards synchronously under the pulling force of the two sliding grooves 50, the two sliding blocks 5 slide inwards to drive the outer end of the chain ring 41 to slide inwards along the generatrix of the conical surface, and simultaneously, in the process that the push-pull device 8 pulls the two conical disks 1 outwards to gradually move away from each other, the sliding sleeve 6 synchronously slides upwards on the transmission shaft 3, and the synchronous sliding of the sliding sleeve 6 enables the central shaft 2 to drive the chain winding shaft 21 to rotate around the chain 4; under the synchronous action of the rotation of the winding chain shaft 21 for winding the chain 4 and the inward sliding of the outer end of the chain ring 41, the chain length wound on the winding chain shaft 21 is gradually increased, and the chain length and the diameter of the chain ring 41 are gradually decreased. If the angular velocity of the outside world input through the center shaft 3 and transmitted to the rotation of the chain ring 41 is not changed in this process, the linear velocity of the rotation of the chain ring 41 is gradually reduced due to the gradual reduction of the diameter and the circumference of the chain ring 41.

As shown in fig. 14 and 17, in the process of changing the length of the circumference of the chain ring 41 by operating the push-pull 8 and the slide bush 6 to extend or shorten, the magnitude of the operation is controlled so that the length of the circumference of the chain ring 41 changed at each operation cycle is equal to an integral multiple of the links, so that the interval between adjacent chain rollers 411 on the chain ring 41 located near the slide groove 50 is equal to the interval between adjacent chain rollers 411 on other portions of the entire chain ring 41.

The invention also discloses a variable diameter chain wheel transmission, which is further described by the following second embodiment, third embodiment and fourth embodiment:

for convenience of visual explanation, the parts and components in the following embodiments that are the same as those in the first embodiment are all described by using the same reference numerals as those in the first embodiment.

Example two

As shown in fig. 19 to 21, the variable diameter chain wheel transmission disclosed by the present invention in this embodiment mainly comprises a set of variable diameter chain wheels 111 and gears. One side of the reducing chain wheel 111 is provided with a gear; the gear consists of a disc 9 and teeth 91. As shown in fig. 22, the gear teeth 91 of the gear are retractable movable teeth; a plurality of tooth holes are formed in the periphery of the wheel disc 9, and the wheel teeth 91 are arranged in the tooth holes; the outer end structure of gear teeth 91 can mesh with the links of chain ring 41; a spring is arranged in the wheel disc 9, the upper end of the spring is abutted against the bottom of the wheel teeth 91, and the lower end of the spring is abutted against the inner wall of the wheel disc 9; the gear teeth 91 can slide in the tooth holes. As shown in fig. 19 to 21, the gears are mounted on the gear shafts; gear carriers 92 are respectively arranged at two ends of the gear shaft; the carrier 92 has a rectangular frame-like structure; a shaft sleeve 93 is arranged in the gear rack 92, and two ends of the gear shaft are arranged on the shaft sleeve 93; the sleeve 93 can slide in parallel left and right in the carrier 92. A pressure spring 95 is arranged between the shaft sleeve 93 and the gear carrier 92; the pressing of the pressing spring 95 against the bushing 93 causes the gears to abut against the chain ring 41.

As shown in fig. 19 to 21, the gear is a double row or multiple row gear. As shown in fig. 22, the gear and the chain ring 41 are in external engagement with each other; the teeth 91 of the meshing portion are engaged by the adjacent two chain rollers 411; the chain rollers 411 at the meshing portions are engaged by the adjacent two gear teeth 91.

On the basis of the working principle of the variable diameter chain wheel 111 disclosed in the first embodiment, the speed is changed and output in the following way:

as shown in fig. 19 to 21, when the diameter of the chain ring 41 is increased, the chain ring 41 pushes the gear to move outward in synchronization while meshing with the gear; when the diameter of the chain ring 41 is reduced, the compression spring 95 pushes the gear to move inwards synchronously, and the gear and the chain ring 41 are always meshed with each other in the whole process. When the external input and the angular speed transmitted to the chain ring 41 are not changed, if the diameter of the chain ring 41 is changed, the linear speed transmitted to the gear is changed, and because the diameter of the gear is not changed, the angular speed of the gear is changed in the same time, and the rotating speed of the gear output outwards through the gear shaft is changed.

The mode of outwards outputting the rotating speed through the gear shaft can be output through the transmission of the universal joint. The transmission principle of the universal joint is the prior art and is not described in detail herein.

EXAMPLE III

As shown in fig. 23 and 24, in this embodiment, the variable diameter chain wheel transmission disclosed by the present invention mainly includes two sets of left and right variable diameter chain wheels (hereinafter, referred to as a left variable diameter chain wheel 111 and a right variable diameter chain wheel 111, respectively) and gears, which are arranged in parallel. A gear is arranged between the left reducing chain wheel 111 and the right reducing chain wheel 111; the periphery of the gear is simultaneously in tangential meshing with a chain ring of the left reducing chain wheel 111 (simply called as the left chain ring 41) and a chain ring of the right reducing chain wheel 111 (simply called as the right chain ring 41).

On the basis of the working principle of the first embodiment and the second embodiment, the present embodiment is operated and shifted as follows:

as shown in fig. 23 and 24, the diameter of the right chain ring 41 gradually decreases as the diameter of the left chain ring 41 gradually increases, and the gears synchronously move to the right under the pushing action of the diameter increase of the left chain ring 41; conversely, as the diameter of the left chain loop 41 gradually decreases, the diameter of the right chain loop 41 gradually increases while the gears synchronously shift to the left. Due to the transmission function of the gears, the linear speed of the right chain ring 41 and the linear speed of the left chain ring 41 are always equal. In the process that the diameter of the left chain ring 41 is gradually increased and the diameter of the right chain ring 41 is gradually decreased, if the external input is the constant angular velocity of the left variable diameter chain wheel 111, the linear velocity of the rotation of the left chain ring 41 is gradually increased; meanwhile, the linear velocity of the right chain ring 41 is gradually increased due to the fact that the linear velocity of the right chain ring 41 is equal to the linear velocity of the left chain ring 41, and the angular velocity of the right chain ring 41 is gradually increased due to the fact that the diameter of the right chain ring 41 is gradually decreased and the linear velocity is gradually increased, so that the angular velocity of the right variable diameter chain wheel 111 which outputs outwards is gradually increased. Similarly, the principle that the output angular velocity becomes smaller can be used for reverse thrust. The advantages of this embodiment over the second embodiment are: the speed change range is larger; and a gear transmission piece between the left reducing chain wheel 111 and the right reducing chain wheel 111 does not need an external auxiliary device to move the gear left and right during transmission.

Example four

In addition to the above embodiments, as shown in fig. 25, the transmission member of the variable diameter sprocket transmission disclosed by the present invention can also adopt a transmission belt 44 fitted with the chain ring 41 to be sleeved on the chain ring 41 for transmission speed change; the principle is similar to that of the CVT continuously variable transmission in the prior art, and the details are not described here.

Claims

1. A reducing chain wheel (111), characterized in that: mainly comprises two conical discs (1) which are coaxially opposite, a chain (4) between the conical discs (1), and a chain rolling shaft (21) in a central through hole of the conical discs (1); the conical surfaces of the two conical disks (1) are opposite, and a sliding groove (50) is arranged in the direction of a generatrix of each conical surface; the chain (4) is arranged on the chain winding shaft (21), the inner end of the chain (4) is connected to the chain winding shaft (21), the outer end of the chain (4) extends from the space between the two conical discs (1) from inside to outside, and the extended part is circumferentially wound on the two conical surfaces to form a chain ring (41); the roller chain shaft (21) can rotate relative to the conical discs (1), and at least one of the two conical discs (1) can axially move relative to the roller chain shaft (21).

2. The variable diameter sprocket (111) of claim 1, wherein: a notch (10) is formed in the inner end of the conical disc (1), and the central through hole of the conical disc (1) is communicated with the conical surface through the notch (10); the notch (10) is adjacent to the chute (50); both sides of the chain section extending from inside to outside between the conical discs (1) pass through the gap (10).

3. The variable diameter sprocket (111) of claim 1, wherein: the sliding block (5) matched with the sliding groove (50) is arranged in the sliding groove (50), the sliding block (5) is clamped in the sliding groove (50), the sliding block (5) can slide in the sliding groove (50), and the outer end of the chain ring (41) is directly or indirectly connected to the sliding block (5).

4. The variable diameter sprocket (111) of claim 1, wherein: a central shaft (2) is arranged at one end or two ends of the coil chain shaft (21), and the coil chain shaft (21) is directly or indirectly axially connected with the central shaft (2).

5. The variable diameter sprocket (111) of claim 1, wherein: a chain drum (33) is arranged between the chain rolling shaft (21) and the conical disc (1), and the chain drum (33) is sleeved on the periphery of the chain rolling shaft (21) and can rotate relatively between the chain rolling shaft and the conical disc; the conical disc (1) is sleeved on the periphery of the chain drum (33), and one end or two ends of the chain drum (33) are directly or indirectly provided with the transmission shaft (3).

6. The variable diameter sprocket (111) of claim 5, wherein: the transmission shaft (3) is integrally of a cylindrical structure.

7. The variable diameter sprocket (111) as in claim 4 or 5 or 6, wherein: the transmission shaft (3) is sleeved on the periphery of the central shaft (2) and can rotate relatively between the transmission shaft and the central shaft; the central shaft (2) is provided with at least one spiral groove hole (20) or straight groove hole (30); the transmission shaft (3) is provided with at least one straight slotted hole (30) or spiral slotted hole (20); a push rod (7) or a ball is arranged in the spiral groove hole (20) or the straight groove hole (30).

8. A reducing chain wheel transmission is characterized in that: comprises the variable diameter chain wheel (111) of claim 1 and a transmission piece, wherein the transmission piece is arranged on one side of the variable diameter chain wheel (111); the transmission piece is a gear or a transmission belt matched with a chain ring (41) of the reducing chain wheel (111).

9. The variable diameter sprocket transmission of claim 8, wherein: the reducing chain wheel (111) is provided with a left set and a right set in parallel, the transmission part is arranged between the left set and the right set of the reducing chain wheel (111), and the transmission part is in transmission contact with the chain rings (41) on the two reducing chain wheels (111) in a matched manner.