WO2010117146A2

WO2010117146A2 - Belt-type continuously variable transmission

Info

Publication number: WO2010117146A2
Application number: PCT/KR2010/001715
Authority: WO
Inventors: 조윤규
Original assignee: Cho Yoon Kyu
Priority date: 2009-04-07
Filing date: 2010-03-19
Publication date: 2010-10-14
Also published as: DE112010001538T5; JP2012522954A; BRPI1011260A2; JP5713994B2; GB201116984D0; CN102428297B; GB2483569A; CN102428297A; GB2483569B; WO2010117146A3

Abstract

The present invention relates to a belt-type continuously variable transmission, and more particularly, to a belt-type continuously variable transmission comprising a variable driving pulley with a variable diameter for controlling a transmission ratio, and a variable slave pulley which is connected to the variable driving pulley via a belt, and which has a diameter that varies by the operation opposite that of the variable driving pulley to adjust the tension of the belt, wherein each of said variable driving pulley and said variable slave pulley has a pair of pulley disks coupled to a pulley shaft, a plurality of belt supports with belt stopper ratchet gears are inserted between the pulley disks such that the belt supports are rotatable in the radial direction, transmission disks are arranged at the outer surfaces of the respective pulley disks such that the transmission disks rotate in opposite directions by a transmission disk rotating device to move the plurality of belt supports in a radial direction, and the belt has ratchet gears which are alternately formed at the inner surface thereof to engage with the respective belt stopper ratchet gears of the belt supports of the variable driving pulley and of the variable slave pulley. The present invention enables the diameters of the variable driving pulley and the variable slave pulley to be varied in an easier and smoother manner, to enable more accurate and efficient stepless changes in gear ratios, and to prevent a slipping phenomenon between the pulley and the belt even in the event of big loads, thus improving the efficiency of power transmission.

Description

Beltless CVT

The present invention relates to a belt-type continuously variable transmission, and more particularly, the diameter of the belt is connected to a variable drive pulley and a variable drive pulley for controlling the speed ratio while the diameter is changed by an operation opposite to the variable drive pulley to control the tension of the belt. A belt type continuously variable transmission comprising a variable driven pulley to be adjusted, wherein the variable driving pulley and the variable driven pulley have a plurality of belt supports formed with a belt latch ratchet gear portion in a radial direction between a pair of pulleys coupled to a pulley shaft. The pulley plate is installed to be movable and the outer surface of each pulley plate is configured to be provided with a shift plate for moving the plurality of belt supports in a radial direction while rotating in opposite directions by a shift plate rotating device, wherein the belt has a variable drive on an inner circumferential surface thereof. On the belt latch ratchet gear formed on the belt support of the pulley and variable driven pulley By configuring the interlocking ratchet gear parts to be formed alternately, the diameters of the variable drive pulley and the variable driven pulley can be changed more easily and smoothly, enabling more accurate and efficient stepless shifting and at the same time when a large load is applied. Even the slip phenomenon between the pulley and the belt is prevented to realize more efficient power transmission.

In general, continuously variable transmission (CVT) continuously shifts between the best and the lowest speed ratios according to a given shift pattern, so that the driving force generated from the engine can be utilized as efficiently as possible to achieve excellent power performance and fuel economy improvement. Speaks the device to help.

Such continuously variable transmissions are widely used in various industrial sites such as automobiles, industrial machines, hoists, goods conveying conveyors, winches, elevators, and escalators. Conventional continuously variable transmissions often have a complicated structure and frequently cause breakdowns. In particular, although it is called a continuously variable speed shift without a shift stage, the actual range of the shift is extremely limited as the structure itself is shifted to a stepped stage, and thus there is a problem in that it is not properly applied according to various uses.

As a conventional continuously variable transmission, a V-belt continuously variable transmission 100 as shown in FIG. 1 is widely used, and the V-belt continuously variable transmission 100 has a drive shaft directly receiving output from an engine ( In the axial direction on the outer periphery of the drive shaft 101 to form a drive side V-groove 104 together with the drive side pulley plate 102 fixed to the outer periphery of the 101 and the drive side fixed pulley plate 102. Variable drive pulley 107 consisting of a drive side hydraulic pulley 103 that is installed to be movable and a drive side hydraulic cylinder 106 that forms a drive hydraulic chamber 105 on the back of the drive side movable pulley 103. And a driven side fixing pulley 109 and a driven side fixing pulley 109 fixedly installed at an outer circumference of the driven shaft 108 disposed at a predetermined remote position in parallel with the driving shaft 101. Axially at the outer periphery of the driven shaft 108 to form an i-side V-shaped groove 111 Variable driven pulley 114 composed of a driven side hydraulic pulley 110 and a driven side hydraulic cylinder 113 which forms a driving hydraulic chamber 112 on the back of the driven side movable pulley 110. The V-belt 115 is installed to be caught between the driving side V-shaped groove 104 of the variable drive pulley 107 and the driven side V-shaped groove 111 of the variable driven pulley 114.

The conventional V-belt type CVT configured as described above applies constant hydraulic pressure to the drive hydraulic chamber 105 of the drive side hydraulic cylinder 106 through a flow path formed inside the drive shaft 101 to drive the movable side pulley plate 103. ) In the axial direction to narrow the width of the drive side V-groove 104 of the variable drive pulley 107 and at the same time drive hydraulic chamber of the driven side hydraulic cylinder 113 through a flow path formed in the driven shaft 108 ( A constant hydraulic pressure is applied to 112 to move the driven side pulley plate 110 in the axial direction to widen the width of the driven side V-shaped groove 111 of the variable driven pulley 114, or vice versa of the variable drive pulley 107. While widening the driving side V-groove 104 and narrowing the width of the driven V-groove 111 of the variable driven pulley 114, the V-belt 115 is applied to the variable drive pulley 107 and the variable driven pulley 114. By changing the contact radius of), the speed ratio is formed.

However, the conventional V-belt continuously variable transmission configured as described above has a large load because the V-belt 115 that is caught by the variable drive pulley 107 and the variable driven pulley 114 is in frictional contact with the pulley. When caught, the slip phenomenon occurs between the variable drive pulley 107 and the variable driven pulley 114 and the V-belt 115, so that power transmission is not smoothly performed, and the slip phenomenon causes the V-belt. There was also a problem that the durability of the 115 is significantly reduced, and also because the tension of the V-belt 115 is easily weakened by repeated use, it is difficult to achieve efficient power transmission.

The present invention is to solve the above problems, the diameter of the variable drive pulley and variable drive pulley for controlling the speed ratio is connected to the belt and the belt is adjusted to the tension of the belt while the diameter is changed by the operation opposite to the variable drive pulley A belt type continuously variable transmission comprising a variable driven pulley, wherein the variable driving pulley and the variable driven pulley are provided with a plurality of belt supports formed with a belt latch ratchet gear between a pair of pulleys coupled to the pulley shaft in a radial direction. Inserted and installed on the outer surface of each pulley plate is installed so that the transmission plate for moving the plurality of belt support in the radial direction while rotating in the opposite direction by the transmission plate rotation device, the belt is variable drive pulley and variable on the inner peripheral surface Meshes with the belt catching ratchet gears formed on the belt support of the driven pulley The ratchet gears are alternately formed so that the diameters of the variable drive pulleys and the variable driven pulleys can be changed more easily and smoothly, allowing for more accurate and efficient stepless shifting, even when a large load is applied. It is a technical task to prevent slippage between the pulley and the belt so as to realize more efficient power transmission.

The present invention for achieving the above technical problem is a variable drive pulley and a variable drive pulley for controlling the speed ratio while the diameter is variable, the variable to control the tension of the belt while varying the diameter in the opposite operation to the variable drive pulley In the belt-type continuously variable transmission comprising a driven pulley, the variable drive pulley is coupled to both ends of the pulley plate coupling portion formed in the center of the outer peripheral surface, and the pulley shaft insertion hole is formed through the pulley shaft insertion hole in the center of the pulley shaft coupling portion respectively A pair of pulley plates radially inserted between the pulley plate and a plurality of slide grooves are formed around the shaft insertion hole so as to be radially movable, and a belt latch ratchet gear part is formed on an outer surface thereof and the pulleys are formed at both ends. To the outer surface of the slide section and the pulley plate respectively inserted into the slide groove of the plate The pulley shaft is inserted into the center part to be rotatably installed on the outer surface of the pulley plate coupled to both ends of the pulley plate coupling portion of the pulley shaft, respectively, with a plurality of belt supports having protruding guide protrusions. A pair of transmission plates having radially formed a plurality of involute curve grooves each having a ball formed therethrough and a plurality of belt support guides inserted between the pulley plates around the pulley shaft insertion hole, respectively; It consists of a variable speed plate rotating device for rotating the shifting plate installed on the outer surface of each of the rotational direction in the opposite direction to move a plurality of belt supports inserted between the pulley plate in the radial direction, wherein the variable driven pulley is the variable drive pulley Made of the same structure as, provided on the outer surface of the belt support of the variable driven pulley The latching ratchet gear portion is formed to be opposite to the inclination direction of the belt latching ratchet gear portion formed on the belt support of the variable driving pulley, and the belt is formed on the inner peripheral surface of the belt latching ratchet gear portion formed on the belt support of the variable driving pulley. The driving side ratchet gear portion and the driven side ratchet gear portion engaged with the belt latching ratchet gear portion formed on the belt support of the variable driven pulley are alternately formed.

In addition, the present invention is that the transmission plate rotating device is respectively installed in the center of the outer surface of the transmission plate is formed through the through-hole through which the pulley shaft penetrates the front and rear, and the oil chamber on both sides of the interior of the oil chamber formed therein A partition partitioning into two spaces is fixedly installed oppositely, and a rotor is coupled to an outer circumferential surface of a pulley shaft inserted through the housing and rotated together with the pulley shaft in an oil chamber divided into two spaces by the partition wall. A pair of hydraulic actuators installed at both sides of the outer circumferential surface of the rotor and configured to protrude to form a vane for dividing the oil chamber divided into two spaces by four partitions into four spaces, and a hydraulic actuator coupled to the transmission plate, respectively. A plurality of through-formed rotors inserted into the interior of each housing of the hydraulic actuator to apply A hydraulic flow path formed in the pulley shaft to communicate with an oil outflow hole of the oil outflow port, and an oil outflow port rotatably inserted and installed on one side of the outer circumferential surface of the pulley shaft to communicate with the hydraulic flow path formed in the pulley shaft. do.

As described above, the belt-type continuously variable transmission according to the present invention is connected to a variable drive pulley and a variable drive pulley for controlling the speed ratio while the diameter is variable, so that the diameter is changed by an operation opposite to the variable drive pulley to control the tension of the belt. It consists of a variable driven pulley, wherein the variable drive pulley and the variable driven pulley is a plurality of belt support formed in the belt latch ratchet gear portion formed between the pair of pulleys coupled to the pulley shaft is installed radially movable and each pulley The outer surface of the plate is configured to be provided with a shift plate for moving the plurality of belt support in the radial direction while rotating in the opposite direction by the shift plate rotating device, the belt is a belt support of the variable drive pulley and variable driven pulley on the inner peripheral surface The ratchet gear parts which are respectively engaged with the belt latching ratchet gear parts formed in the shaft are alternately As it is configured to be formed, by using the shifting plate rotated in the opposite direction by the shifting plate rotation device, it is possible to change the diameter of the pulley more easily and smoothly, which enables more accurate and efficient stepless shifting as well. Even if a large load is applied, slippage is prevented from occurring between the pulley and the belt, so that more efficient power transmission can be realized.

1 is an explanatory diagram showing a conventional V-belt type continuously variable transmission.

2 is a perspective view showing a belt-type continuously variable transmission according to the present invention.

3 is a perspective view showing a belt used in the belt type CVT according to the present invention.

Figure 4 is an exploded perspective view showing the configuration of the variable drive pulley and variable driven pulley of the belt-type continuously variable transmission according to the present invention.

Figure 5 is an exploded perspective view showing the configuration of the hydraulic actuator used for the variable drive pulley and the variable driven pulley of the belt-type continuously variable transmission according to the present invention.

Figure 6 is a cross-sectional view showing the assembled state and the hydraulic supply line of the variable drive pulley and the variable driven pulley of the belt-type continuously variable transmission according to the present invention.

7 and 8 are explanatory views showing the operation of the belt continuously variable transmission according to the present invention.

Hereinafter, the present invention for achieving the above object will be described in detail with reference to FIGS. 2 to 8.

Belt continuously variable transmission according to the present invention is connected to the variable drive pulley 10 and the variable drive pulley 10 and the belt 50 to control the speed ratio while the diameter is variable as shown in Figure 2 variable drive pulley ( It is made of a variable driven pulley 30 to adjust the tension of the belt 50 while the diameter is variable by the operation opposite to 10).

Since the variable drive pulley 10 and the variable driven pulley 30 are made of the same structure except for some components, the same components are denoted by the same reference numerals, and the different components are denoted by different symbols. It will be described separately.

As shown in FIG. 4, the variable drive pulley 10 includes a pulley shaft 11 having a pulley plate coupling portion 11a formed at the center of the outer circumferential surface thereof.

At this time, it is preferable that the pulley plate coupling portion 11a formed at the center of the outer circumferential surface of the pulley shaft 11 is formed integrally with the pulley shaft 11, but for the convenience of manufacturing, the pulley plate coupling portion 11a is separately provided. It is also possible to be configured to assemble to the pulley shaft 11 after manufacturing as a part.

A pair of

pulley plates

14a and 14b are coupled to both ends of the pulley plate coupling portion 11a of the pulley shaft 11 by fastening means such as fixing bolts, respectively, of each

pulley plate

14a and 14b. A pulley shaft insertion hole 12 is formed through the center portion, and a plurality of slide grooves 13 are radially formed around the pulley shaft insertion hole 12.

Further, a plurality of belt supports 15 are inserted between the

pulley plates

14a and 14b so as to be movable in a radial direction. On the outer surface of each belt support 15, a ratchet gear portion 15a for catching belts is provided. Are formed and guide protrusions 15c protruding to the outer surfaces of the slide portions 15b and the

pulley plates

14a and 14b respectively inserted into the slide grooves 13 of the

pulley plates

14a and 14b at both ends. Is formed.

In this case, the plurality of slide grooves 13 respectively formed in the

pulley plates

14a and 14b may be radially formed around the pulley shaft insertion hole 12, but a straight line passing through the center of the pulley plate may be formed. It is preferable to form each inclined so as to form a constant angle with respect to, and the inclination angle is preferably selected to an appropriate value within the range of 0 to 90 degrees depending on the size, size, and application range of the continuously variable transmission.

As such, a plurality of slide grooves 13 formed in the

pulley plates

14a and 14b, respectively, are formed radially about the pulley shaft insertion hole 12, but have a constant angle with respect to a straight line passing through the center of the pulley plate. When the belt latching ratchet gear portion 15a formed on the outer surface of the belt support 15 is formed to be inclined at the same time as the angle, the insertion is installed between the slide grooves 13 corresponding to each other in parallel. As the plurality of belt supports 15 come into contact with the belt 50 while moving in a radial direction in a state inclined by the angle with respect to the axial center line of the pulley shaft 11, the outer surface of the plurality of belt supports 15 Since the belt latching ratchet gear portion 15a formed in the belt catching ratchet gear portion 15a does not come into contact with the belt 50 at once, the belt catching ratchet gear portion 15a sequentially contacts the belt 50 from one side of the belt latching ratchet gear portion 15a. In addition to reducing the impact and noise generated when the plurality of belt supports 15 and the belt 50 come into contact with each other in the process of shifting while being variable, the shift can be made more stable even at high speed. do.

In addition, the number of the belt support 15 is equal to the number of pulleys equal to the minimum diameter of the pulley so as to rotate smoothly in a state in which the belt 50 caught by the pulley is stably supported. Although it is advantageous to form a number, the strength and processing of the size of the belt latching ratchet gear portion 15a formed on the outer surface of the belt support 15 and the slide portions 15b and the guide protrusions 15c provided at both ends thereof. And considering the assembling property, it is preferable to form about 24 pieces.

On the outer surface of the

pulley plates

14a and 14b respectively coupled to both ends of the pulley plate coupling portion 11a of the pulley shaft 11, a pair of

transmission plates

18a and 18b respectively receive the thrust bearings 18. It is installed rotatably in a state of being interposed, the pulley shaft insertion hole 16 is formed through the center portion of each of the shifting plate (18a) (18b), respectively, and the pulley plate (14a) around the pulley shaft insertion hole (16) A plurality of involute curve grooves 17 into which the guide protrusions 15c of the plurality of belt supports 15 inserted between the 14b are respectively inserted are radially formed.

At this time, a plurality of grooves 17 formed to guide the guide protrusions 15c of each belt support 15 to the shifting

plates

18a and 18b are formed in an involute curve shape. The force required for shifting, that is, the rotational force of the shifting

plates

18a and 18b required to move the plurality of belt supports 15 inserted between the

pulley plates

14a and 14b in the radial direction is the diameter of the pulley. This is to enable the transmission with the same rotational force in any range by allowing the belt parts 15 to be uniformly transmitted from the maximum part to the minimum part at all times.

In addition, the

shift plates

18a and 18b rotatably installed on the outer surfaces of the

pulley plates

14a and 14b are rotated in opposite directions by the shift plate rotating device, and the

pulley plates

14a and 14b are rotated. The plurality of belt supports 15 inserted therebetween are moved in the radial direction.

A shift plate rotating device for rotating the

shift plates

18a and 18b in opposite directions to each other is coupled to each other at a central portion of an outer surface of the

shift plates

18a and 18b, as shown in FIG. The

hydraulic actuators

24a and 24b of the

hydraulic actuators

25a and 24b and the hydraulic oil passages 25 formed in the pulley shaft 11 to apply hydraulic pressure to the

hydraulic actuators

24a and 24b. The oil outflow port 26 is rotatably inserted into one side of the outer circumferential surface of the pulley shaft 11 so as to communicate with the hydraulic oil passage 25.

The pair of

hydraulic actuators

24a and 24b constituting the speed change plate rotating device are respectively installed in the center of the outer surface of the

speed change plates

18a and 18b, and as shown in FIG. A through hole 19 through which the pulley shaft 11 penetrates is formed in the partition wall 21a for dividing the oil chamber 20 into two spaces on both sides of the housing 21 in which the oil chamber 20 is formed. 21b) is fixedly installed to face the inside of the oil chamber 20 divided into two spaces by the

partitions

21a and 21b on an outer circumferential surface of the pulley shaft 11 inserted through the housing 21. The rotor 22 which is coupled to rotate together with the pulley shaft 11 is inserted and installed, and the oil chamber 20 divided into two spaces by

partitions

21a and 21b on both sides of the outer circumferential surface of the rotor 22. The

vanes

23a and 23b for dividing the into four spaces are configured to protrude.

At this time, the

partition walls

21a and 21b and the rotor 22 which are installed inside the housing 21 are divided by the

vanes

23a and 23b of the

partition walls

21a and 21b and the rotor 22. Oil seals 27 and 28 for sealing four spaces are respectively installed.

In addition, a plurality of

oil outflow holes

22a and 22b are formed through the outer circumferential surface of the rotor 22, and the

oil outflow holes

22a and 22b are formed by oil grooves formed in the inner circumferential surface of the rotor 22. The hydraulic passage 25 formed in the pulley shaft 11 is in communication with each other.

The hydraulic passage 25 is for applying stable hydraulic pressure to the

hydraulic actuators

24a and 24b which rotate together with the pulley shaft 11, and the hydraulic actuators 24a which are coupled to and installed on the shifting

plates

18a and 18b, respectively. It is formed in the pulley shaft 11 so as to communicate with a plurality of

oil outflow holes

22a, 22b penetrating through the rotor 22 inserted into each housing 21 of the (24b).

The oil outflow port 26 is for connecting the hydraulic supply device to the hydraulic flow path 25 formed in the pulley shaft 11 rotating at a constant speed, the hydraulic oil formed in the pulley shaft 11 It is rotatably inserted into one side of the outer circumferential surface of the pulley shaft 11 so as to communicate with the furnace 25.

At this time, a pair of

oil outflow holes

26a and 26b are formed through the outer circumferential surface side of the oil outflow port 26, and the

oil outflow holes

26a and 26b are inner peripheral surfaces of the oil outflow port 26. The oil groove is formed in the communication with the hydraulic passage 25 formed in the pulley shaft (11).

And, as shown in Figure 6, the hydraulic supply line of the transmission plate rotating apparatus, through the oil outflow hole 26a of the oil outflow port 26 is rotatably inserted into one side of the outer peripheral surface of the pulley shaft (11). The second hydraulic oil introduced into the hydraulic actuator 24a and the hydraulic actuator 24b through the first hydraulic flow path 25a formed in the pulley shaft 11, respectively, and then introduced into the pulley shaft 11. Oil returned through the oil outlet port 26b of the oil outlet port 26 via the furnace 25b or oil introduced through the oil outlet port 26b of the oil outlet port 26 is inside the pulley shaft 11. An oil outflow port 26 flows into the hydraulic actuator 24b and the hydraulic actuator 24a through the second hydraulic flow path 25b formed therein, and then through the first hydraulic flow path 25a formed in the pulley shaft 11. It is configured to return through the oil outflow hole (26a) of).

On the other hand, the variable driven pulley 30 is made of the same structure as the variable drive pulley 10, as shown in Figure 2 belt provided on the outer surface of the belt support 31 of the variable driven pulley 30 The latching ratchet gear portion 31a is configured to be formed opposite to the inclination direction of the belt latching ratchet gear portion 15a formed on the belt support 15 of the variable driven pulley 10.

At this time, the belt latching ratchet gear portion 15a provided on the outer surface of the belt support 15 of the variable drive pulley 10 and the outer surface of the belt support 31 of the variable driven pulley 30 are provided. The belt latching ratchet gear portion 31a is preferably formed to be shifted from each other without being formed on the same line so as to reduce the shock during shifting and maintain a more stable and balanced belt locking state.

That is, as shown in Figure 2, if the belt latching ratchet gear portion 15a of the variable drive pulley 10 is formed on both sides of the outer surface of the belt support 15, belt latch of the variable driven pulley 30 The ratchet gear portion 31a for the belt is formed at the center of the outer surface of the belt support 31, and conversely, the belt latching ratchet gear portion 15a of the variable drive pulley 10 is centered on the outer surface of the belt support 15. When formed in, the belt latching ratchet gear portion 31a of the variable driven pulley 30 is formed on both sides of the outer surface of the belt support 31.

In addition, the belt 50 has a drive side ratchet gear portion 51 and a variable driven pulley engaged with the belt latching ratchet gear portion 15a formed on the belt support 15 of the variable drive pulley 10 on an inner circumferential surface thereof. The driven side ratchet gear portion 52 meshing with the belt catching ratchet gear portion 31a formed on the belt support 31 of 30 is configured to be alternately formed.

In this case, the belt 50 may be formed in the form of a flat belt or a link belt, and in the case of forming the belt 50 in the form of a flat belt, the same material as the existing belt is used. It is preferable to form with a metal material, synthetic resin or carbon fiber material in order to improve the durability or durability.

When the belt 50 is formed in the form of a link belt, as shown in FIG. 3, the belt catching ratchet gear portion 15a formed on the belt support 15 of the variable drive pulley 10 is fitted. A driven side ratchet gear engaged with a plurality of link plates 53 having a driving side ratchet gear portion 51 and a belt latching ratchet gear portion 31a formed on the belt support 31 of the variable driven pulley 30. It is preferable that the plurality of link plates 54 having the portion 52 formed thereon are connected by the link pins 55.

In addition, the driving side ratchet gear unit 51 and the driven side ratchet gear unit 52 provided on the inner circumferential surface of the belt 50 may have a belt latching ratchet gear unit 15a and a variable driven pulley of the variable drive pulley 10. It is preferable to form so as to correspond to the position of the belt latching ratchet gear part 31a of 30, respectively.

That is, as shown in FIGS. 2 and 3, the belt latching ratchet gear portion 15a of the variable drive pulley 10 and the belt latching ratchet gear portion 31a of the variable driven pulley 30 are belt supports. If formed on both the outer side of the outer surface of the (15) and the center of the outer surface of the belt support 31, respectively, the drive side ratchet gear portion 51 and the driven side ratchet gear portion 52 provided on the inner peripheral surface of the belt 50 is a belt The inner peripheral surface of the 50 and the center of the inner peripheral surface, respectively, formed on the contrary, the belt latching ratchet gear portion 15a of the variable drive pulley 10 and the belt latching ratchet gear portion 31a of the variable driven pulley 30. Is formed on the center of the outer surface of the belt support 15 and on both sides of the outer surface of the belt support 31, respectively, the drive side ratchet gear portion 51 and the driven side ratchet gear portion 52 provided on the inner circumferential surface of the belt 50. ) Are formed on the inner circumferential surface center and the inner circumferential surface both sides of the belt 50, respectively.

Referring to the operational relationship of the belt-type continuously variable transmission according to the present invention configured as described above are as follows.

The beltless continuously variable transmission according to the present invention connects a hydraulic supply device (not shown) to an oil outlet port 26 of a variable speed plate rotation apparatus installed in the variable drive pulley 10 and the variable driven pulley 30, respectively. By operating the 24a) and 24b respectively, the diameter of the pulley can be easily and smoothly changed.

That is, in order to reduce the diameter of the variable drive pulley 10 maintaining the maximum diameter as shown in Fig. 7 (a) (b), it rotates on one side of the outer peripheral surface of the pulley shaft 11. Coupling to the central portion of the outer surface of the transmission plate (18a) (18b) through the oil outflow hole (26a) of the oil outflow port (26) and the first hydraulic flow path (25a) formed inside the pulley shaft (11). The oil is supplied to the installed

hydraulic actuators

24a and 24b.

The oil supplied to the hydraulic actuator 24a coupled to the center portion of the outer surface of the shift plate 18a is plural oil outflow holes 22a formed through the rotor 22 as shown in FIG. The hydraulic pressure flows into the first space 20a and the third space 20c of the oil chamber 20 formed in the housing 21 through the

partition walls

21a and 21b fixedly installed in the housing 21. The hydraulic pressure is applied to the

partition walls

21a and 21b fixedly installed in the housing 21 by the oil introduced into the first space 20a and the third space 20c of the oil chamber 20. As a result, oil stored in the second space 20b and the fourth space 20d of the oil chamber 20 flows out through the oil outflow hole 22b of the rotor 22, and the housing 21 rotates. As the 21 rotates, the transmission plate 18a coupled to the housing 21 rotates clockwise.

In addition, the oil supplied to the hydraulic actuator 24a coupled to the center of the outer surface of the shift plate 18b operates the hydraulic actuator 24b so that the shift plate 18b coupled to the hydraulic actuator 24b is provided. Rotate counterclockwise.

At this time, the shifting plate (18a) (18b) is installed so that the rotor 22 installed in each housing 21 of the hydraulic actuator (24a, 24b) intersect in a U-shape, that is, the hydraulic actuator (24a) Rotor 22 is installed so that the

vanes

23a and 23b face the 5 o'clock and 11 o'clock directions, respectively, and the rotor 22 of the hydraulic actuator 24b has the

vanes

23a and 23b each 1 van. As it is installed to face the direction and 7 o'clock, each time the hydraulic pressure is applied to the hydraulic actuator (24a, 24b) is rotated in the opposite direction to each other.

When the

shift plates

18a and 18b are rotated in opposite directions by the

hydraulic actuators

24a and 24b, the belt is inserted into the involute curve groove 17 of the

shift plates

18a and 18b. As the rotational force is applied to the guide protrusion 15c of the support 15, and the rotational force of the shifting

plates

18a and 18b is applied to the guide protrusions 15c formed at both ends of the belt support 15, respectively. Since the slide portion 15b of the belt support 15 moves along the slide groove 13 of the

pulley plates

14a and 14b in the direction of the center of the pulley, the variable drive formed by the plurality of belt supports 15 is driven. The diameter of the pulley 10 can be easily and smoothly reduced.

Subsequently, in order to increase the diameter of the reduced variable drive pulley 10 as shown in FIG. 8A (b), the oil outflow port is rotatably installed on one side of the outer peripheral surface of the pulley shaft 11. A hydraulic actuator 24a coupled to an outer surface center portion of the

transmission plates

18a and 18b through the oil outflow hole 26b of the 26 and the second hydraulic flow path 25b formed inside the pulley shaft 11, respectively. Oil is supplied to 24b.

The oil supplied to the hydraulic actuator 24a coupled to the center portion of the outer surface of the shift plate 18a is formed in the housing 21 through the plurality of oil outlet holes 22b formed through the rotor 22. The hydraulic pressure is applied to the

partition walls

21a and 21b fixedly installed in the housing 21 while flowing into the second space 20b and the fourth space 20d of the 20, and the second of the oil chamber 20. As the hydraulic pressure is applied to the

partition walls

21a and 21b fixedly installed inside the housing 21 by the oil flowing into the space 20b and the fourth space 20d, the first space of the oil chamber 20 ( As the oil stored in the 20a and the third space 20c flows out through the oil outlet hole 22a of the rotor 22, the housing 21 rotates, and the housing 21 rotates as the housing 21 rotates. The shifting plate 18a that is engaged is rotated counterclockwise.

In addition, the oil supplied to the hydraulic actuator 24b coupled to the outer surface center portion of the shift plate 18b operates the hydraulic actuator 24b, and thus the shift plate 18b coupled to the hydraulic actuator 24b. ) Will rotate clockwise.

When the

shift plates

18a and 18b are rotated in opposite directions by the

hydraulic actuators

24a and 24b, the belt is inserted into the involute curve groove 17 of the

shift plates

plates

18a and 18b is applied to the guide protrusions 15c formed at both ends of the belt support 15, respectively. The slide portion 15b of the belt support 15 is moved along the slide groove 13 of the

pulley plates

14a and 14b in the opposite direction of the pulley center, so that the variable formed by the plurality of belt supports 15 The diameter of the drive pulley 10 can be easily and smoothly increased.

On the other hand, the variable driven pulley 30 is installed in the installation direction of the rotor 22, respectively installed in the hydraulic actuator (24a, 24b) opposite to the variable drive pulley (10) hydraulic actuator (24a, 24b) When the hydraulic pressure is applied to the

transmission plates

18a and 18b respectively rotate in the opposite direction to the variable drive pulley 10, when the diameter of the variable drive pulley 10 increases, the diameter decreases and the variable drive pulley 10 is increased. When the diameter of the) decreases to operate opposite to the variable drive pulley 10 to increase the diameter.

In this way, the variable driven pulley 30 is smoothly adjusted by the tension of the belt 50 is caught between the variable drive pulley 10 and the variable driven pulley 30 by changing the diameter in the opposite operation to the variable drive pulley 10. It becomes possible.

Therefore, the belt-type continuously variable transmission according to the present invention can more easily and smoothly change the diameters of the variable drive pulley 10 and the variable follower pulley 30, thereby enabling more accurate and efficient continuously variable transmission.

In addition, the belt type continuously variable transmission according to the present invention has a drive side ratchet gear portion 51 formed on one side of the inner circumferential surface of the belt 50 formed on the outer surface of the plurality of belt supports 15 provided in the variable drive pulley 10. The belt formed on the outer surface of the plurality of belt supports 31 provided on the variable driven pulley 30 with the driven side ratchet gear portion 52 formed on the other side of the inner circumferential surface while being firmly engaged with the belt latching ratchet gear portion 15a. Since the rotating ratchet gear portion 31a is firmly engaged with the latching ratchet gear part 31a, slipping between the pulley and the belt can be effectively prevented even when a large load is applied.

In addition, the belt-type continuously variable transmission according to the present invention forms a wide width of the variable drive pulley (10) and the variable driven pulley (30) and at the same time belt latch ratchet formed on the outer surface of the belt support (15) (31), respectively The size of the transmission is easily increased by increasing the number of belts 50 caught between the positions of the

gear parts

15a and 31a and between the variable drive pulley 10 and the variable driven pulley 30. Since it can be made, it can be applied to devices used in various industrial sites such as ships, hoists, goods transfer conveyors, winches, elevators and escalators as well as automobiles.

According to the present invention, the diameters of the variable drive pulleys and the variable driven pulleys can be changed more easily and smoothly, enabling more accurate and efficient continuously variable shifting and slipping between the pulleys and the belt even under a large load. This invention relates to a belt type continuously variable transmission that prevents this from happening and enables more efficient power transmission.

Claims

The variable diameter of the belt 50 is controlled by the variable driving pulley 10, the variable driving pulley 10, and the belt 50, which control the speed ratio while the diameter is variable, and the diameter thereof is changed by the operation opposite to the variable driving pulley 10. In the belt continuously variable transmission consisting of a variable driven pulley 30 to be adjusted,

The variable drive pulley 10,

A pulley shaft 11 having a pulley plate coupling portion 11a formed at the center of the outer circumferential surface thereof,

It is coupled to both ends of the pulley plate coupling portion (11a) of the pulley shaft 11, the pulley shaft insertion hole 12 is formed through the center portion and the plurality of slide grooves 13 around the pulley shaft insertion hole 12 A pair of pulleys (14a, 14b) formed radially,

A radially movable insert is installed between the pulley plates 14a and 14b, and a belt catching ratchet gear portion 15a is formed on an outer side thereof and slides of the pulley plates 14a and 14b on both ends thereof. A plurality of belt supports 15 formed with slide portions 15b inserted into the grooves 13 and guide protrusions 15c respectively protruding to the outer surfaces of the pulley plates 14a and 14b;

The center portion is rotatably installed on the outer surface of the pulley plate (14a) (14b) coupled to both ends of the pulley plate coupling portion (11a) of the pulley shaft (11) with the thrust bearing (18) interposed therebetween. The pulley shaft insertion hole 16 is formed in each of the guide projections 15c of the plurality of belt supports 15 inserted between the pulley plates 14a and 14b around the pulley shaft insertion hole 16. A pair of transmission plates 18a and 18b each having a plurality of involute curve grooves 17 respectively inserted radially;

A plurality of belt supports inserted between the pulley plates 14a and 14b by rotating the shifting plates 18a and 18b rotatably installed on the outer surfaces of the pulley plates 14a and 14b in opposite directions. 15) is composed of a transmission plate rotating device to move the radially,

The variable driven pulley 30 is made of the same structure as the variable drive pulley 10, the belt latch ratchet gear portion 31a is provided on the outer surface of the belt support 31 of the variable driven pulley 30 It is configured to be formed opposite to the inclination direction of the belt latching ratchet gear portion 15a formed on the belt support 15 of the variable drive pulley 10,

The belt 50 has a drive side ratchet gear portion 51 and a variable driven pulley 30 engaged with the belt latching ratchet gear portion 15a formed on the belt support 15 of the variable drive pulley 10 on an inner circumferential surface thereof. Belt-type continuously variable transmission, characterized in that the driven side ratchet gear portion (52) engaging the belt latching ratchet gear portion (31a) formed on the belt support 31 of the alternately formed.
The method of claim 1,

The shift plate rotating device,

Housings in which the through holes 19 through which the pulley shaft 11 penetrates are formed on the front and rear surfaces of the shifting plates 18a and 18b, respectively, and the oil chamber 20 is formed therein. 21. An oil chamber divided into two spaces by the partition walls 21a and 21b is fixedly installed so as to face the partition walls 21a and 21b for dividing the oil chamber 20 into two spaces. The rotor 22 which is coupled to the outer circumferential surface of the pulley shaft 11 inserted to penetrate the housing 21 and rotates with the pulley shaft 11 is inserted into the interior of the rotor 21, and both sides of the outer circumferential surface of the rotor 22 are inserted. The pair of hydraulic actuators 24a and 24b configured to protrude from vanes 23a and 23b for dividing the oil chamber 20 divided into two spaces by the partitions 21a and 21b into four spaces. )Wow,

To the rotor 22 inserted into each housing 21 of the hydraulic actuators 24a and 24b to apply hydraulic pressure to the hydraulic actuators 24a and 24b respectively coupled to the transmission plates 18a and 18b. A hydraulic oil passage 25 formed in the pulley shaft 11 so as to communicate with the plurality of oil outflow holes 22a and 22b formed therethrough;

Belt type stepless endless, characterized in that consisting of the oil outflow port 26 is rotatably inserted into one side of the outer peripheral surface of the pulley shaft 11 to communicate with the hydraulic flow passage 25 formed in the pulley shaft 11 Transmission.