KR20090060400A - Cvt using a belt having improved durability - Google Patents

Abstract

A CVT using a belt having improved durability is provided to prevent the load from being concentrated upon the center by differing the center direction of the centrifugal force member from the center of the driving part. The diameter of the driving par(1) of the variable pulley is changed by the centrifugal force of the driving shaft(11). The driven part(2) of the variable pulley shape is formed of the structure which is identical with the driving part. The belt(6) transmits the power transmission between the driven part and the driving part. The oil controlling part(3) controls the driving part of the variable pulley shape and the diameter of the driven part. The driving part has a space part for charging the oil. The cylindrical rotation axis(12) of the hollow tube shape is formed.

Description

CVT using a belt having improved durability}

The present invention relates to a continuously variable transmission that can be continuously shifted from a relationship of a driving part having a variable diameter by centrifugal force and a driven part which is connected in such a way as to receive power from the driving part and a belt, the diameter being inversely proportional to the driving part. Stepless speed change is possible, but the oil adjusting part is constituted between the driving part and the driven part to adjust the diameter of the driving part and the driven part, and in particular, the force is applied to the driven part by limiting the width at which the driven part is changed during the operation of the low end. The purpose of the present invention is to provide a continuously variable transmission that can be provided, as well as a continuously variable transmission which is more durable than a conventional transmission.

The present invention relates to a continuously variable transmission, and more particularly, the continuously variable transmission includes: a variable pulley type driving unit having a variable diameter in response to centrifugal force of a rotating drive shaft by direct transmission of power;

A driven part of a variable pulley type configured to be spaced apart from each other by a same structure as the driving part;

A belt for power transmission between the driving portion and the driven portion and for the diameters to be inversely proportional to each other;

It relates to a continuously variable transmission using a belt with improved durability, characterized in that the variable pulley type driving portion and the oil adjusting portion that can adjust the diameter of the driven portion.

In general, continuously variable transmissions are used in various places such as hoists, conveyors for transporting goods, raw materials, elevators, and escalates, depending on the use in automobiles and various industrial sites. Although it is called a continuously variable transmission, since the actual structure itself is close to the stepped speed change, the transmission is extremely limited, and thus it is not properly applied according to the use, and it is accompanied with problems such as high incidence of failure during use due to the complicated structure.

On the other hand, in the case of automatic transmission for automobiles, there is a problem of excessive power loss and very high failure rate by using torque converter as a substitute for clutch. This is not good, the consumption of fuel is not only due to the loss of unnecessary power, but also the production cost is excessive because of the large number of parts, the repair and repair is very difficult when the failure occurs, the burden of the repair cost is very high, especially The structure is very complicated and the number of parts is very heavy, which leads to problems such as fuel loss.

In addition, in order to supplement the above-mentioned disadvantages of the conventional continuously variable transmission, the present applicant filed on February 28, 2006 and described in detail with reference to the accompanying drawings, the contents of which are registered as a Patent No. 10-0749279 dated August 7, 2007. As follows.

It has a space to fill the oil inside, and the center of one side is the driving shaft where the power is input, and the center of the other side is the rotatable pulley which plays the role of the center of rotation of the hollow tube-type rotating shaft composed of a passageway through which oil can travel. A plurality of self-contained cylinders formed on the circumferential surface of the cylinder and the radially protruding due to the centrifugal force generated by the rotation of the drive shaft, and the end of which is formed with a belt groove in which the belt can be seated; A drive unit coupled to the link and configured by a pair of linear bushings each having a linear motion on the drive shaft and the gray bottom shaft;

A driven part having the same structure at a spaced distance from the driving part;

A belt which is seated in a belt groove formed in the self-cylinder of the driving unit and a belt groove formed in the self-cylinder of the driven unit to transmit power of the driving unit to the driven unit;

Both ends are jointly coupled to the rotating shaft of the drive unit and the rotating shaft of the driven unit, characterized in that it is composed of an oil control unit for adjusting the oil filled in the driving cylinder and the filled oil of the driven unit.

In addition, the contents of the improved technology registered in the Utility Model No. 20-0443988 filed on March 23, 2007 and filed on July 12, 2007 by improving the continuously variable transmission having the above-described configuration are described in the following description. The housing is formed on both sides of the drive unit and the driven part is formed with a guide lane for guiding the role in order to improve the orientation of the self-cylinder when radially deployed.

Since the continuously variable transmission has the above-described configuration, the shift is automatically and gradually shifted compared to the conventional transmission, so that there is no impact of shifting, thereby ensuring comfortable driving performance, and the engine life is extended because the engine maintains relatively even rotation. have.

Nevertheless, it is inevitable that the durability of the xylin, which has a configuration that is unfolded in multiple stages by the centrifugal force in the aforementioned continuously variable transmission, is unavoidable, and furthermore, to increase the transmission ratio, more steps are required to increase the speed ratio. It should be unfolded, but it is relatively poor in durability as compared to integrally constructed.

The present invention has been made in order to compensate for the above-mentioned drawbacks, by integrally producing a radially unfolded cylinder from the cylinder to produce a linear reciprocating linear movement from the inside of the cylinder to shift than the speed ratio of the conventional continuously variable transmission The aim is to provide a continuously variable transmission with a wide range and durability.

The continuously variable transmission using the belt which improves the durability of the present invention has a conventional multi-cylinder is unfolded in multiple stages, while the transmission of the present invention is made of a piston to reciprocate the inside and outside of the cylinder to improve the durability In addition, it has a large speed change range in the form of a piston reciprocating linearly in and out of the cylinder, and loads the center point by shifting the center direction of the centrifugal force member radially spread from the center point of the drive unit to form a rotating body together with the piston. This prevents concentration and has the advantage of being more durable.

The present invention relates to a continuously variable transmission, and more particularly, the continuously variable transmission includes: a variable pulley type driving unit having a variable diameter in response to centrifugal force of a rotating drive shaft by direct transmission of power;

A driven part of a variable pulley type configured to be spaced apart from each other by a same structure as the driving part;

A belt for power transmission between the driving portion and the driven portion and the diameters thereof are inversely proportional to each other;

It relates to a continuously variable transmission using a belt with improved durability, characterized in that the variable pulley type driving portion and the oil adjusting portion that can adjust the diameter of the driven portion.

When described in detail with the attached to the continuously variable transmission using a belt having improved durability of the present invention having the above-described configuration and object as follows.

1 is a perspective view of a continuously variable transmission of the present invention, Figure 2 is a perspective view of the one side guide plate and the belt of the continuously variable transmission of the present invention, Figure 3 is a front view showing a state in which the belt is fastened in FIG.

As shown in FIG. 1, the continuously variable transmission of the present invention is a variable pulley type drive unit 1 having a variable variable diameter by a centrifugal force of a drive shaft 11 rotating by direct transmission of power, and the drive unit 1. A variable pulley type driven part 2 constructed in the same structure and spaced apart at regular intervals, a power transmission between the drive part 1 and the driven part 2, and a belt 6 so that diameters are inversely proportional to each other; It is characterized in that it consists of an oil control unit (3) that can adjust the diameter of the rotating body of the drive unit (1) and the driven part (2) of the variable pulley form.

Accordingly, the power input from the drive shaft 11 is a value that is variably changed according to the relationship between the drive unit 1 and the driven unit 2 through the driven shaft 21.

4 is a schematic diagram of a continuously variable transmission of the present invention.

Prior to the description, reference numerals 131 and 231 denote oil inlets of the cylinders 13 and 23 of the driving unit 1 and the driven unit 2 respectively, which flow from the rotating shafts 12 and 22.

And T represents the tension pulley to adjust the tension.

4 is a schematic diagram of the continuously variable transmission according to the present invention. Referring to the operation process and principles of the continuously variable transmission of the present invention, the drive unit configured to change the diameter by centrifugal force generated while rotating by the drive shaft 11 that receives power directly and rotates ( 1) and the driven part 2 by the belt 6 having the same structure as the drive part 1 and the driven part 2 connected to receive power from the drive part 1 to the belt with a limited length. It is changed to be inversely proportional to the diameter of.

In the above-described driving principle, the diameter of the driving unit 1 is changed by the centrifugal force, so that the cylindrical cylinder 13 having the space S for filling the oil 5 therein is centered on one surface of the power directly. The center of the drive shaft 11 and the other surface receiving the transmission is composed of a rotating shaft 12 of the hollow tube form configured with a passage through which oil (5) can come and go inside the cylinder 13 by the rotation of the drive shaft (11) Has a structure in which the drive shaft 11 and the rotation shaft 12 are rotated about the center axis.

The space part is shown by the letter S, which stands for Space.

In addition, the cylinder 13 includes a pair of pistons 14 which are inserted into the cylinder 13 filled with the oil 5 and protrude outwardly.

The pair of pistons 14 are preferably configured to face in opposite directions to each other.

This is because the radial force with the centrifugal force member 15 to be described later to achieve a balance of forces when forming a rotating body.

When the cylinder 13 is rotated by the rotation of the drive shaft 11, the piston 14, which is configured to protrude outward from the inside of the cylinder 13, is more extended outward as the centrifugal force is larger.

However, due to the characteristics of the pulley, the driving unit 1 should be made in the shape of a rotating body, but since the pair of pistons 14 are difficult to form a rotating body, the piston 14 is formed on the outer circumferential surface of the cylinder 13 by centrifugal force. ) Is composed of a plurality of centrifugal force members (15) which are expanded together in the circumferential direction of the cylinder (13) when protruded outward.

The centrifugal force member 15 and the piston 14 are moved to the same length while receiving the same force by the distribution device 16 to be described later to form a complete rotating body shape.

The piston 14 is a rod 142 that linearly reciprocates in and out of the cylinder 13 by centrifugal force, and is integrally formed with the rod 142 and is always located on the outer side of the cylinder 13. It is composed of a head portion 141 having a heavier weight than the rod 142 in order to double the centrifugal force.

In addition, the head portion 141 is formed with a relatively larger area than the rod 142 and the end portion located in the inner side of the cylinder 13 of the rod 142 and the locking jaw to prevent the departure from the cylinder It would be even more desirable to have the same shape.

Since the shape of the locking jaw is a general shape, it is not covered in detail.

And the inside of the cylinder 13 is formed to have a space (S) divided into two by symmetrical diameter passing through the center, the space (S) is divided into two is that the piston 14 is When protruding to the outside of the cylinder 13, when accurately expressed, the rod 142 of the piston 14 has a longer stroke length and extends to the centrifugal force at the time of protruding and extending from the inside of the cylinder 13 to the outside. As a result, when the rod 142 protrudes outward, the piston 14 may have a directionality capable of reciprocating only in one direction that is driven by centrifugal force.

If the cross-sectional shape of the rod 142 is manufactured in an oval shape, the shape of the space S may also be a space S having a height in the cross-sectional shape of the rod 142. It is preferable to be produced by the space S.

In addition, if the centrifugal force member 15 is composed of the same shape and the same material as the head portion 141 of the piston 14, the centrifugal force member 15 can receive the same centrifugal force by the distribution device 16 together with the piston 14. Rotating body is formed by expanding radially can be formed more stably.

The end portion of the head portion 141 and the centrifugal force member 15 of the piston 14 is provided with a plurality of belt grooves 19 on which the belt 6 to be described later is seated. The guide member 18 of the protruding form seated on the lane 171 is comprised.

Figure 5 is a perspective view showing the drive side of the continuously variable transmission of the present invention, Figure 6 is a detailed perspective view of a portion of the drive side of the present invention, Figure 7 is a partial perspective view showing the relationship between the guide member and the guide lane of the present invention.

As shown in FIGS. 2 and 6, the dispensing device 16 has one end coupled to a hinge 163 formed on an upper surface of the guide member 18, and the other end thereof has the driving shaft 11 and the rotating shaft ( A hinge 163 having the same number of hinges 163 formed on the head portion 141 of the piston 14 and the centrifugal force member 15 on the outer surface of the pair of linear bushings 161 capable of linear movement on 12). The piston 14 and the centrifugal force member 15 are equally movable by the links 162 coupled to one-to-one corresponding to each other.

The guide member 18 is configured to protrude on both sides of the head portion 141 and the centrifugal force member 15 of the piston 14, the linear bushing 161 has a constant thickness and length Branches must be manufactured in the form of hollow tubes one-to-one with the hinge 163 formed on the outer surface of the linear bushing 161 and the hinge 163 formed on both sides of the head portion 141 and the centrifugal force member 15 of the piston 14. Correspondingly coupled links 162 may be formed to have the same length distribution in the same length.

It is thought that the configuration of the distribution device 16 is reminiscent of an umbrella rod, so that it is easy to understand.

Referring to the operation and principle of the distribution device 16 in more detail as follows.

When the piston 14 and the centrifugal force member 15 are radially unfolded by the centrifugal force, the hinge 163 formed on the upper surface of the guide member 18 configured to protrude on both sides of the piston 14 and the centrifugal force member 15. ) Is coupled to the link 162 is moved in the vertical direction and the other side of the link 162 is configured on the outer surface of the linear bushing 161 that can linearly reciprocate on the drive shaft 11 and the rotating shaft 12 Since it is also coupled to the hinge 163, as the link 162 moves closer to the vertical, the linear bushing 161 also moves linearly toward the cylinder 13 side.

If the piston 14 and the centrifugal force member 15 protrude less from the cylinder 13 than at a high speed at the low speed, the linear bushing 161 moves linearly to a position away from the cylinder.

At this time, since the hinge 163 formed on the upper surface of the guide member 18 and the hinges 163 formed on the linear bushing 161 are formed in the same number and correspond one to one, respectively, the linear bushing 161 is provided. The piston 14 and the centrifugal force member 15 are also radially unrolled by the same length as the length of the linear reciprocating motion.

In particular, the guide plate 17 is formed on both sides of the cylinder is formed with a guide lane 171 which serves as a guide to move more stably when the piston 14 and the centrifugal force member 15 radially unfolded or retracted by the centrifugal force ) Is configured.

The guide plate 17 is preferably configured in a disk shape to favor the rotation, the guide lane 171 to guide the guide plate 17 is a guide member 18 of the piston 14 and the centrifugal force member 15. It is preferable that they are formed in the circumferential direction at the center of the guide plate 17 as the through holes constituted by the same number.

The guide member 18 of the protruding form configured on both sides of the piston 14 and the centrifugal force member 15 is seated on the guide lane 171 of the through-hole type and the piston 14 and the centrifugal force member ( 15 is moved by the length of the guide lane 171.

Therefore, the width of the guide member 18 to the width of the guide lane 171 is inserted into the fit so that the piston 14 and the centrifugal force member 15 is moved more stably when radially unfolded.

The driven part 2 having the same configuration as the driving part 1 is formed at a point spaced apart from the driving part 1, and the piston 24 and the centrifugal force member 25 of the driven part 2 are formed. A plurality of belt grooves 29 on which the belt 6 can be seated are formed at the end surface of the belt.

The operation of the distribution device 26 by the combination of the linear bushing 261, the hinge 263, and the link 262 of the driven part 2 is the same as the operation process of the distribution device 16 on the driving part 1 side. Therefore, detailed description is omitted.

Of course, the guide member 28 is also formed on the side of the driven part 2 in the same manner as the configuration of the driving part 1 and is seated on the guide lane 271 formed on the guide plate 27 on the driven part 2 side. The diameter of the rotating body on the side will change stably.

Accordingly, the belt formed on the end face of the piston 14 and the centrifugal force member 25 of the driven part 2 and the belt groove 19 formed on the end face of the piston 14 and the centrifugal force member 15 of the driving part 1. According to the magnitude of the power transmitted to the drive shaft 11 by the belt 6 seated in the groove 29, the diameter of the rotating body formed by the drive unit 1 and the diameter of the rotating body formed by the driven unit 2 are mutually different. Inverted variable pulley form.

It is preferable that a plurality of belt grooves 19 and 29 be formed to mount a plurality of belts 6 so that even a relatively large amount of power can be transmitted without difficulty, and a V belt is used to obtain a large friction force.

The belt grooves 19 and 29 may be slightly changed in shape depending on the conditions of the driving means.

In addition, the piston 14 and the centrifugal force member 15 on the drive unit 1 side are manufactured to have a weight about three times heavier than the piston 24 and the centrifugal force member 25 on the driven unit 2 side. ) Can be more effectively affected by the centrifugal force than the driven part (2).

8 is a schematic view showing the orientation of the guide lane of the present invention.

As shown in FIG. 8, the pistons 14 and 24 unfold in opposite directions, as described above, have a balance of force because the inner shapes of the cylinders 13 and 23 are configured to be symmetrical with respect to the diameter as a reference line. In order to draw a pair of pistons 14 and 24 and an imaginary circle A whose diameter is the length to the center of the pistons 14 and 24, the centerline B of the pistons 14 and 24 is connected to the imaginary circle A. It can also be called tangent.

Therefore, the centers of all the guide lanes 171 and 271 are formed to form a line segment in contact with the virtual circle A. FIG.

This prevents the force from being biased at one point of the center of the cylinder 13, 23 by making the center of the cylinder 13, 23 subjected to the force wider, and tangential to contact all the directions of the force with the imaginary circle A. By doing this, the power can be balanced.

At this time, it is preferable that the tangential direction of the guide lanes 171 and 271 is tangent to the outer line segment of the virtual circle A if the rotation of the driving unit 1 side rotates in the direction of the arrow as shown in FIG.

3, the rotational direction of the driving unit 1 is the direction of the force for pulling the belt 6 in the tension relationship between the belt 6 caught on the driving unit 1 side and the belt 6 hanging on the driven unit 6 side. Therefore, the rotational direction and the tangential direction of the drive unit 1 are the same, so that the cylinder 13 is not forced to improve the durability of the cylinder 13 and at the same time, the force of pulling the belt 6 is doubled. do.

In some cases, the tension may be adjusted by the tension pulley T shown in FIG. 4.

If the pistons 14 and 24 of the drive unit 1 and the driven unit 2 protrude from the inside of the respective cylinders 13 and 23 by centrifugal force, the insides of the respective cylinders 13 and 23 have an empty space S. The oil 5 is filled into the cylinders 13 and 23 of the driving part 1 and the driven part 2 due to the action of the oil adjusting part 3 to be described later in the empty space part S. It can withstand strong loads.

9 is a schematic view showing a high speed state of the oil control unit of the continuously variable transmission of the present invention, Figure 10 is a schematic view showing a low speed state of the oil control unit of the continuously variable transmission of the present invention, Figure 11 is an oil control unit of the continuously variable transmission of the present invention. A schematic diagram showing the power state.

As shown in FIGS. 9 to 11, the oil adjusting unit 3 is configured between the rotating shaft 12 of the driving unit 1 and the rotating shaft 22 of the driven unit 2, and the driving unit 1 and the driven unit. By adjusting the amount of oil (5) coming and going into the cylinder (13, 23) of (2) it is possible to adjust the diameter of the drive unit 1 and the driven part (2).

The configuration of the oil control unit 3 is coupled to the rotary shafts 12 and 22 of the driving unit 1 and the driven unit 2 by the joint 4, respectively, a fixed tube 31 in which oil 5 is filled therein, Located in the inner space of the fixed tube 31 in the longitudinal direction of the elastic spring 32 and the driving portion (1) of the both ends of the elastic spring 32 in the fixed direction in the longitudinal direction with the oil (5) And an elastic control plate 33 having a through hole 331 formed therein so that oil 5 flowing into the fixed tube 31 of the oil adjusting unit 3 from the driving unit 1 can freely travel with the fixed tube 31. ) Is located on the driven part (2) side of both ends of the elastic spring (32) in the inside of the can be moved inside the fixed tube 31 by hydraulic pressure so that oil (5) from the driven part (2) freely It is characterized by consisting of a compression plate 34 formed in a partition form.

When explaining the configuration and principle of the above-described oil control unit 3 in more detail, both ends of the fixed tube 31 having a space in which the oil 5 can be filled therein, respectively, of the driving unit 1 and the driven unit 2, respectively. It is coupled by the rotary shafts 12 and 23 and the joint 4.

Therefore, the oil 5 in the cylinders 13 and 23 of the driving unit 1 and the driven unit 2 described above is configured to be able to travel to and from the fixed tube 31 through the respective rotation shafts 12 and 22. do.

Here, the fixing tube 31 is a fixed shaft and the drive unit 1 and the rotating shafts 12 and 22 are shafts configured to rotate, and the joint 4 connecting the fixed shaft and the rotating shaft is suitable for a special situation. Since the joint 4 should be used and a variety of joints suitable for a particular situation as in the present invention have been developed, the shape of the joint will not be described in detail, and only the joint 4 will be named.

An elastic spring 32 which is supported in the longitudinal direction is seated inside the fixing tube 31, and an elastic member 32 is provided on both sides of the driving part 2 of both ends of the elastic spring 32 supported by the inside of the fixing tube 31. The compression plate 34 is configured on the driven part 2 side of the adjustment plate 33.

The above-described elastic control plate 33 is a thin plate shape is formed with a through-hole 331 through which the oil (5) can freely come and go so as not to be affected by the oil (5) flowing into the fixed tube (31), The compression plate 34 is in the form of a thin diaphragm formed so that oil cannot freely travel inside the fixed tube 31.

Therefore, the oil 5 on the drive unit 1 side and the oil 5 on the driven unit 2 side are separated by the compression plate 34, and the fixed tube of the oil control unit 3 from the drive unit 1 ( 31 is introduced into the oil (5) through the through hole 331 of the elastic control plate 33 does not affect the elastic spring 32, but if the oil (5) is to be introduced from the driven portion (2) Since the compression plate 34 blocks the side of the driven part 2 in a diaphragm form so that the oil 5 can not come and go, the oil 5 enters the inside of the fixed tube 31 together with the compression plate 24 due to hydraulic pressure. The inflow of oil 5 from the driven part 2 acts to compress the elastic spring 32 because it is pushed in and out.

FIG. 9 is a schematic view showing the inside of the oil adjusting unit in a high speed state. As shown in FIG. 9, when the driving shaft 11 rotates at a high speed, the driving unit 1 is greatly affected by the centrifugal force, and thus the cylinder of the driving unit 1 The piston 14 from the inside of the 13 protrudes outward, wherein the hydraulic pressure in the cylinder 13 of the drive unit 1 is lowered and is relatively connected to the drive unit 1 and the belt 6. The cylinder 23 on the driven part 2 side is increased in inverse proportion to the hydraulic pressure so that the hydraulic pressure on the driven part 2 side is directed to the fixed tube 31 of the oil adjusting part 3.

Then, the compression 34 plate formed on the driven part 2 side of the fixed pipe 31 of the oil adjusting part 3 compresses the elastic spring 32 of the fixed pipe 31 by hydraulic pressure on the driven part 2 side. While pushing to the driving unit 1 side.

Therefore, the diameter of the rotating body formed by the drive unit 1 is large, and the diameter of the rotating body formed by the driven unit 2 is relatively small, thereby forming a form suitable for high speed.

FIG. 10 is a schematic view showing the inside of the oil control unit in a low speed state. On the contrary, when the drive shaft 11 is changed from high speed rotation to low speed, the centrifugal force generated on the drive unit 1 side is reduced, so that the elastic spring 32 has a restoring force as shown in FIG. The compression spring (34) is restored by the compression by pressing the compression plate 34 to the driven part 2 side and the compression plate 34 is the cylinder of the driven part (2) the oil (5) side of the driven part (2) (23) It is pushed to the inside, and the piston 24 in the cylinder 23 naturally protrudes to the outside, so that the diameter of the rotating body on the driven part 2 side becomes large.

Therefore, the diameter of the rotating body formed by the drive unit 1 becomes smaller, and the diameter of the rotating body formed by the driven unit 2 becomes larger, which is suitable for low speed.

11 is a schematic view showing the inside of the oil control unit in the power state, when the elastic control plate 33 is pushed into the inside of the fixed tube 31 by using the elastic control lever 35 connected to the switch that can be operated in the driver's seat. The elastic spring 32 is compressed by pushing the elastic spring 32 toward the driven part 2 without affecting the oil 5 filled in the fixed tube 31 by the through hole 331 formed in the elastic control plate 33.

Accordingly, since the change in the movement of the oil 5 on the driven part 2 side is small as much as the elastic spring 32 is compressed and set in the fixed tube 31 to the driven part 2 side, the drive shaft 11 Even if the power is transmitted to the rpm, the diameter of the rotating body on the driven part 2 side is prevented from being minimized, thereby enabling the operation of the continuous power state.

Since the elastic control lever 35 can be configured to simply push the elastic control plate 33 by the operation of the switch configured in the driver's seat, the form is not discussed in detail.

1 is a perspective view of a continuously variable transmission of the present invention.

Figure 2 is a perspective view omitting one side guide plate and the belt of the continuously variable transmission of the present invention.

Figure 3 is a front view of fastening the belt in FIG.

4 is a schematic diagram of a continuously variable transmission of the present invention.

Figure 5 is a perspective view showing the drive side of the continuously variable transmission of the present invention.

6 is a detailed perspective view of a part of the drive unit side of the present invention.

7 is a partial perspective view showing the relationship between the guide member and the guide lane of the present invention.

8 is a schematic view showing the orientation of the guide lane of the present invention.

Figure 9 is a schematic diagram showing a high speed state of the oil control unit of the continuously variable transmission of the present invention.

10 is a schematic view showing a low speed state of the oil control unit of the continuously variable transmission of the present invention.

Figure 11 is a schematic diagram showing the power state of the oil adjusting portion of the continuously variable transmission of the present invention.

<Description of Signs of Major Parts of Drawings>

1. Drive 2. Driven 3. Oil Control

4. Joint 5. Oil 6. Belt

11. Drive shaft 12. Rotary shaft 13. Cylinder

14. Piston 15. Centrifugal force member 16. Distribution device

17. Guide plate 18. Guide member 19. Belt groove

141.Head 142.Rod

161.Linear bushing 162. Link 163. Hinge

171. Guide Lane

21. Driven shaft 22. Rotary shaft 23. Cylinder

24. Piston 25. Centrifugal Force Member 26. Distribution Device

27. Guide plate 28. Guide member 29. Belt groove

31. Fixed tube 32. Elastic spring 33. Elastic control plate

34. Compression Plate 35. Elastic Control Lever

241. Head 242. Rod

261.Linear bushings 262. Links 263. Hinge

271.Guide Lanes

331. Opening

Claims (14)

In the continuously variable transmission, The transmission includes a drive unit (1) of variable pulley type whose diameter varies variably by centrifugal force of the drive shaft (11) rotating by direct transmission of power; A driven part 2 of a variable pulley type configured to be spaced apart from each other by a same structure as the driving part; A belt (6) for power transmission between the drive unit (1) and the driven unit (2) and a diameter in inverse proportion to each other; Endless transmission using a belt with improved durability, characterized in that the variable pulley-type drive unit (1) and the oil control unit (3) that can adjust the diameter of the driven part (2). The method of claim 1, The drive unit 1 has a space for filling the oil 5 therein, the center of one side is the drive shaft 11 to which power is transmitted, the center of the other surface is the passage so that the oil (5) can come and go inside A cylinder 13 configured with a rotating shaft 12 having a hollow tube shape; A pair of pistons (14) formed so as to protrude outward from the cylinder (13) by a centrifugal force from the inside of the cylinder (13) and protruding in opposite directions; A plurality of centrifugal force members (15) radially expanded together with the cylinder (13) to form a rotating body when the piston (14) protrudes out of the cylinder (13) by centrifugal force; Endless transmission using a belt with improved durability, characterized in that the piston (14) and the centrifugal force member (15) is composed of a distribution device (16) to be unfolded in the same length at the same time with the same force when radially deployed to form a rotating body. The method of claim 2, The inside of the cylinder 13 is formed to have a space portion S having a shape divided into two by symmetrical diameter passing through the center so that the piston 14 protrudes outward from the space portion S by centrifugal force. Endless transmission using a belt with improved durability, characterized in that it has a long stroke as long as possible, and configured to have one direction when the piston 14 protrudes outward by centrifugal force. The method of claim 2, The piston 14 is composed of a rod 142 linearly reciprocating in and out of the cylinder 13 by centrifugal force, and integrally with the rod 142, which is always located on the outer side of the cylinder 13 to provide centrifugal force. Endless transmission using a belt with improved durability, characterized in that consisting of a head portion 141 having a heavier weight than the rod 142 in order to double the. The method of claim 2, Durable, characterized in that the belt groove (19) on which the belt 6 can be seated at the end surface of the head (141) of the piston (14), and the guide member (18) of protruding shape is formed at both side portions. Continuously variable transmission with improved belt. The method according to claim 4 and 5, The centrifugal force member (15) is a continuously variable transmission using a belt having improved durability, characterized in that it has the same shape as the head portion (141) of the piston (14). The method of claim 2, The dispensing device 16 is coupled to a hinge 163, one end of which is formed on the upper surface of the guide member 18, and the other end of the pair is linearly movable on the drive shaft 11 and the rotating shaft 12 The piston 14 is connected to the hinge 163 formed on the upper surface of the guide member 18 on the outer surface of the bushing 161 by a link 162 coupled one-to-one to each other. And a centrifugal transmission member using a belt having improved durability, characterized in that the centrifugal force member (15) receives the same force and can move the same. The method of claim 2, The piston 14 and the centrifugal force member 15 formed on the drive unit 1 side are manufactured to have a weight that is relatively heavier than the piston 24 and the centrifugal force member 25 on the driven unit 2 side. Endless transmission using a belt with improved durability, characterized in that configured to be more affected by the centrifugal force than the driven portion (2). The method of claim 1, Guide lanes 171 act as guides when the diameters of the rotating body formed by the drive unit 1 and the driven unit 2 are changed by centrifugal force on both sides of the drive unit 1 and the driven unit 2 of the variable pulley type. Stepless transmission using a belt with improved durability characterized in that the formed guide plate (17). The method of claim 9, The guide lane 171 is formed in the form of through holes formed in the same number as the piston 14 and the centrifugal force member 15 to have a length in the circumferential direction at the center of the guide plate, and the direction of rotation of the drive shaft 11 and Continuously variable transmission using a belt with improved durability characterized in that the configuration is inclined in the same direction. The method according to claim 5 and 10, The guide member 18 having a protruding shape formed on the side surfaces of the piston 14 and the centrifugal force member 15 of the driving unit 1 and the driven unit 2 is inserted into the guide lane 171 to fit the guide lane ( Continuously variable transmission using a belt with improved durability characterized by moving along. The method of claim 1, The oil adjusting unit 3 is a cylinder of each of the driving unit 1 and the driven unit 2 through an oil passage formed inside the rotating shaft 12 of the driving unit 1 and the rotating shaft 22 of the driven unit 2. (13, 23) A continuously variable transmission in which the speed range is characterized by being able to adjust the diameter of the rotating body of the drive unit 1 and the driven unit 2 by adjusting the amount of oil flowing in and out. The method of claim 12, The oil control unit 3 is coupled to the rotary shafts (12, 22) of the drive unit (1) and the driven unit (2), respectively, by a joint (4) fixed tube 31 is filled with oil (5) therein; An elastic spring 32 held in the longitudinal direction together with the oil 5 filled in the internal space of the fixed tube 31; In the fixing pipe 31, the through hole may be located at the driving unit 1 side of the both ends of the elastic spring 32 so that the oil 5 flowing into the inside of the fixing tube 31 from the driving unit 1 may freely travel. 331 and the elastic control plate 33 is formed; It is located on the driven part (2) side of the both ends of the elastic spring 32 in the fixed pipe 31 is movable in the fixed pipe 31 by hydraulic pressure, but oil (5) can freely come and go from the driven part (2) Continuously variable transmission using the belt is characterized by consisting of a compression plate of the plate form so as not to improve durability. The method of claim 13, The elastic control plate 33 can be forcibly moved in the fixed tube 31 by the elastic control lever 35 to improve the durability characterized in that the elastic spring can be adjusted by compressing or releasing the elastic spring (32). CVT with belt.

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