WO2025193039A1 - Belt-type gear transmission for interlocking and controlling driving side and following side - Google Patents

Abstract

Disclosed is a belt-type gear transmission for interlocking and controlling the driving side and the following side, wherein the radius of rotation of the driving gear assembly of the driving shaft and that of the following gear assembly of the following shaft are interlocked, controlled, and shifted by linear reciprocating movements in a direction parallel to the driving shaft caused by the piston of a hydraulic device. The belt-type gear transmission according to the present invention comprises: a driving gear assembly installed on a driving shaft; a following gear assembly installed on a following shaft; a belt having a gear formed on the inner surface thereof and configured to connect the driving gear assembly and the following gear assembly such that torque is transferred from the driving shaft to the following shaft; and a transmission controller for controlling the transmission such that the increase/decrease in the size of the radius of rotation of the driving gear assembly is inversely interlocked with the increase/decrease in the size of the radius of rotation of the following gear assembly. The transmission controller comprises: first and second sleeves installed on the driving shaft so as to slide/reciprocate in an axial direction parallel to the driving shaft, the first and second sleeves having threads formed on the outer periphery thereof, respectively; third and fourth sleeves installed on the following shaft so as to slide/reciprocate in the axial direction, the third and fourth sleeves having threads formed on the outer periphery thereof, respectively; an interlocking control table having an H-shape, four corners of the interlocking control table being coupled to the first to fourth sleeves by bearings, respectively; and a hydraulic device having a piston for reciprocating the interlocking control table in the axial direction. The first and second sleeves and the third and fourth sleeves have threads formed on the outer periphery thereof in opposite directions. The transmission controller further comprises a pressurization position adjuster for controlling the hydraulic device to move toward one of the driving gear assembly and the following gear assembly, which has the larger radius of rotation, thereby pressurizing the interlocking control table. The pressurization position adjuster comprises: a guide gear installed in parallel to the axial direction; a guide slot formed on the interlocking control table perpendicularly to the axial direction; a control rod having one end fixed/coupled to the piston so as to reciprocate in the axial direction; a rotary gear hinge-coupled to the other end of the control rod by a rotation constraint pin and configured to mesh with the guide gear; and a rotary arm having one end hinge-coupled to the other end of the control rod by a rotation constraint pin such that same rotates while being constrained by rotation of the rotary gear by means of a key of the rotation constraint pin, the other end of the rotary arm being constrained in the axial direction by the guide slot and is maintained to be movable perpendicularly to the axial direction.

Description

Belt-type gear transmission that controls the driving side and the driven side in conjunction

The present invention relates to a belt-type gear transmission that transmits the rotational power of a driving shaft to a driven shaft, and more specifically, to a belt-type gear transmission that has a plurality of planetary gears arranged at equal intervals at the same distance from the center of the shaft on the driving shaft and the driven shaft, and has a variable rotation radius.

A transmission is a device that changes and transmits the speed or rotational power of an engine or motor, and is generally divided into gear type and friction type.

A gear-type transmission is a continuously variable transmission that transmits power by changing the gear ratio at a certain level, but has the disadvantage of having a limited number of gears and complex gear control.

In comparison, friction transmissions can be implemented as belt-type or toroidal types, and although both of these have the advantage of being continuously variable transmissions with continuously changing gear ratios, they have the disadvantage of significantly increasing frictional loss due to excessive pressure applied to the friction surface to prevent slipping, and making it difficult to transmit large driving forces.

Accordingly, a belt-type gear transmission was developed that can transmit large driving force while having the advantages of a continuously variable transmission by installing multiple planetary gears on the drive shaft and the driven shaft respectively so that the rotation radius of the planetary gears can be changed, and the gears of the planetary gears and the gears of the belt mesh to transmit rotational force.

However, conventional belt-type gear transmissions have not yet been properly commercialized due to various unresolved problems, such as difficulty in controlling the position of the planetary gears during gear shifting, difficulty in precisely meshing the gears of the planetary gears and the gears of the belt at the gear teeth and gear grooves as the rotational radius of the planetary gears continuously changes during the gear shifting process, problem in that the length of the belt connecting the planetary gears of the drive shaft and the planetary gears of the driven shaft changes as the rotational radius of the planetary gears changes, and problem in that an eccentricity phenomenon occurs due to a difference in the rotational radius of the planetary gears at the drive shaft and the driven shaft.

[Prior Art Literature]

(Patent Document 1) Korean Patent Publication No. 10-2012-0010629 (February 6, 2012)

(Patent Document 2) Korean Patent Publication No. 10-2008-0083934 (September 19, 2008)

(Patent Document 3) WO 2012/011739 A2 (January 26, 2012)

The present invention provides a belt-type gear transmission that controls the drive side and the driven side in conjunction with each other by controlling the rotational radius of the drive gear assembly of the drive shaft and the driven gear assembly of the driven shaft through a linear reciprocating motion in a direction parallel to the drive shaft by a piston of a hydraulic device, thereby changing the speed, and also eliminating the change in belt length due to a change in the rotational radius and the eccentricity phenomenon due to the difference in the rotational radius of the drive shaft and the driven shaft.

In order to achieve the above object, a belt-type gear transmission for transmitting the rotational force of a drive shaft to a driven shaft according to the present invention comprises: a drive gear assembly installed on the drive shaft; a driven gear assembly installed on the driven shaft; a belt having gears formed on the inner surface thereof and connecting the drive gear assembly and the driven gear assembly to transmit the rotational force of the drive shaft to the driven shaft; and a transmission controller for controlling transmission so that an increase or decrease in the size of the rotational radius of the drive gear assembly is mutually inversely linked to an increase or decrease in the size of the rotational radius of the driven gear assembly.

In the belt-type gear transmission described above, the transmission controller comprises: first and second sleeves, which are respectively installed on the drive shaft and slide back and forth in an axial direction parallel to the drive shaft, and have threads formed on the outer periphery; third and fourth sleeves, which are respectively installed on the driven shaft and slide back and forth in the axial direction, and have threads formed on the outer periphery; a linkage control member having an H shape and connected to the first to fourth sleeves by bearings at each of the four corners; and a hydraulic device having a piston that causes the linkage control member to reciprocate in the axial direction.

In the above belt-type gear transmission, the screw threads formed on the outer periphery of the first and second sleeves and the third and fourth sleeves are characterized in that they are formed in opposite directions.

In the above belt type gear transmission, the hydraulic device is configured to further include a pressure position adjuster that controls the drive gear assembly and the driven gear assembly to move toward the one with a relatively larger rotation radius to pressurize the linkage control unit.

In the above belt type gear transmission, the pressure position adjuster is configured to include: a guide gear installed in a direction perpendicular to the axial direction; a control rod having a gear meshing with the guide gear on the outer periphery, the control rod being screw-connected with the piston and rotating in response to the linear reciprocating motion of the piston while moving on the guide gear; and a roller groove fixedly connected to the piston, the linkage control rod being constrained in the axial direction and being maintained movable in a direction perpendicular to the axial direction.

In the above belt type gear transmission, the pressure position adjuster is configured to include: a guide gear installed in a direction parallel to the axial direction; a guide slot formed in a direction perpendicular to the axial direction on the linkage control table; a control rod having one end fixedly connected to the piston and reciprocating in the axial direction; a rotary gear hingedly connected to the other end of the control rod by a rotation restraint pin and meshed with the guide gear; and a rotary arm having one end hingedly connected to the other end of the control rod by the rotation restraint pin and being restrained by the rotation of the rotary gear by a key of the rotation restraint pin to rotate, and the other end being restrained in the axial direction by the guide slot and maintained movable in a direction perpendicular to the axial direction.

In the above belt type gear transmission, the first and second linkage control arm arms, each of which has one end fixedly connected to the linkage control arm and the other end provided with an inclined gear; first and second support arms installed on both sides between the driving gear assembly and the driven gear assembly; and first and second roller arms, which are pin-connected to the first and second support arms, respectively, and rotate by the inclined gears while pressing the belt by rollers; and the linear reciprocating motion of the linkage control arm further includes a roller device in which the first and second roller arms rotate within a certain range by the inclined gears of the first and second roller arms corresponding to the inclined gears provided on the first and second linkage control arm arms.

In the above belt type gear transmission, it further comprises first and second linkage control arm arms, each of which is fixedly connected to the linkage control arm at one end and has an inclined gear at the other end; first and second supporters installed on both sides between the driving gear assembly and the driven gear assembly; first and second roller hinge extension bars, each of which has an inclined gear at one end that meshes with the inclined gears of the first and second linkage control arm; and first and second roller arms, each of which is hingedly connected to the first and second supporters, and rotates by the inclined gears installed by the first and second roller hinge extension bars connected to the one end while pressing the belt by rollers provided at the other end.

In the above belt type gear transmission, the first and second roller arms are characterized in that they rotate toward the smaller rotation radius among the drive gear assembly and the driven gear assembly to pressurize the belt.

Figure 1a is a layout diagram showing the overall configuration of a belt-type gear transmission (first embodiment) according to the present invention.

Figure 1b is a layout diagram showing the overall configuration of a belt-type gear transmission (second embodiment) according to the present invention.

Figure 2a is a conceptual diagram for explaining the operation of a belt-type gear transmission (first embodiment) according to the present invention.

Figure 2b is a conceptual diagram for explaining the operation of a belt-type gear transmission (second embodiment) according to the present invention.

Figure 3 illustrates a first fixed plate installed on each of the driving shaft and the driven shaft.

Figure 3a illustrates a second fixed plate installed on each of the driving shaft and the driven shaft.

Figure 4 illustrates the first and second rotary plates installed on the drive shaft.

Figure 4a illustrates the first and second rotary plates installed on the driven shaft.

Figure 5 shows the change in the rotating arm according to the change in the rotation radius when the rotating arm is arranged and connected to the rotating plate.

Figure 6 illustrates each support plate.

Figure 7 illustrates (a) a cross-sectional view, (b) a plan view, (c) a tensioning plate coupled with a tensioning bolt, (d) a plate, (e) a gear piece, (f) a tensioning bolt, and (e) a twisted steel wire for a portion of a belt.

Figure 8a illustrates a comparison of the driving states of the belt-type gear transmission (first embodiment) according to the present invention ((a) when the rotation speed is reduced, (b) when the rotation speed is increased).

Figure 8b illustrates a comparison of the driving states of the belt-type gear transmission (second embodiment) according to the present invention ((a) when the rotation speed is reduced, (b) when the rotation speed is increased).

Fig. 9a illustrates a planar arrangement of a speed controller (first embodiment) with a reinforced pressure position adjuster.

Fig. 9b illustrates a cross-sectional layout of the transmission controller (first embodiment) of Fig. 9a.

Fig. 9c illustrates a planar arrangement of a gear controller (second embodiment) with a reinforced pressure position adjuster.

Fig. 9d illustrates a cross-sectional layout of the gear controller (second embodiment) of Fig. 9c.

Figure 10a is a drawing for explaining the configuration and operation of the roller device (first embodiment).

Figure 10b illustrates the arrangement of a speed controller (first embodiment) with a reinforced roller device.

Figure 10c is a drawing for explaining the configuration and operation of the roller device (second embodiment).

Figure 10d illustrates the arrangement of a speed controller (second embodiment) with a reinforced roller device.

Fig. 11a is a cross-sectional view showing the overall configuration of a planetary gear (first embodiment).

Fig. 11b is a cross-sectional view showing the overall configuration of a planetary gear (second embodiment).

Figure 12a illustrates (a) the inner sleeve, (b) the left pin, and (c) the right pin that constitute the main body in Figure 11a.

Figure 12b illustrates (a) the outer sleeve, (b) the left fixing screw, and (c) the right fixing screw that constitute the gear sleeve in Figure 11a.

Figure 12c illustrates (a) the main spring, (b) the left support plate, and (c) the right support plate that constitute the two-way shock absorber in Figure 11a.

Figure 12d illustrates (a) a compression rod and (b) a pressure regulating pin that constitute the spring pressure regulator in Figure 11a.

Figure 12e illustrates (a) a left rotation pressure ring, (b) a left support ring, (c) an auxiliary spring, (d) a right support ring, and (e) a right rotation pressure ring that constitute the rotation inducer in Figure 11a.

Figure 12f illustrates the rotation auxiliary ring in Figure 11a.

Figure 12g illustrates (a) the left pin and (b) the right pin that constitute the main body in Figure 11b.

Figure 12h illustrates (a) the outer sleeve, (b) the left fixing screw, and (c) the right fixing screw that constitute the gear sleeve in Figure 11b.

Figure 12i illustrates (a) the main spring, (b) the left support plate, and (c) the right support plate that constitute the two-way shock absorber in Figure 11b.

Figure 12j illustrates (a) a compression rod and (b) a pressure regulating pin that constitute the spring pressure regulator in Figure 11b.

Figure 12k illustrates (a) a left rotation pressure ring, (b) a left support ring, (c) an auxiliary spring, (d) a right support ring, and (e) a right rotation pressure ring that constitute the rotation inducer in Figure 11b.

Figure 12l illustrates the rotation auxiliary ring in Figure 11b.

Fig. 13 is a drawing for explaining the rotation and movement of a gear sleeve when a gear equipped on a belt meshes in front of a gear equipped on a planetary gear in the rotational direction.

Figure 13a is a drawing for explaining the rotation and movement of a gear sleeve when a gear equipped on a belt meshes with a gear equipped on a planetary gear at the rear in the direction of rotation.

Figure 14 illustrates the main spring pressure when (a) the driving shaft torque is small and (b) the driving shaft torque is large.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the attached drawings.

Fig. 1a is a layout diagram showing the overall configuration of a first embodiment of a belt-type gear transmission according to the present invention, and Fig. 2a is a conceptual diagram for explaining the operation of the first embodiment of the belt-type gear transmission according to the present invention. Fig. 1b is a layout diagram showing the overall configuration of a second embodiment of a belt-type gear transmission according to the present invention, and Fig. 2b is a conceptual diagram for explaining the operation of the second embodiment of the belt-type gear transmission according to the present invention.

A first embodiment of a belt-type gear transmission according to the present invention comprises a drive gear assembly (10) installed on a drive shaft (1), a driven gear assembly (20) installed on a driven shaft (2), a belt (30), and a shift controller (40), and a second embodiment of a belt-type gear transmission according to the present invention comprises a drive gear assembly (10b) installed on a drive shaft (1), a driven gear assembly (20b) installed on a driven shaft (2), a belt (30), and a shift controller (40b).

Referring to FIGS. 1a, 1b, 2a and 2b, the driving shaft (1) and the driven shaft (2) are installed parallel to each other at positions spaced apart by a certain distance. A plurality of axial grooves (1_1, 2_1) are formed on the outer periphery of each of the driving shaft (1) and the driven shaft (2).

First, referring to FIGS. 1A and 2A, the driving gear assembly (10) includes a plurality of planetary gears (11), first and second fixed plates (12), first and second rotating plates (13), a plurality of rotating arms (14), and respective support plates (15), and the driven gear assembly (20) includes a plurality of planetary gears (21), first and second fixed plates (22), first and second rotating plates (23), a plurality of rotating arms (24), and respective support plates (25). However, the scope of the present invention is not limited thereto, and either the driving gear assembly (10) or the driven gear assembly (20) may be implemented as a gear having a constant rotation radius.

The planetary gears (11) constituting the drive gear assembly (10) are preferably formed with gears that mesh with the gears of the belt (30) on a portion of the outer circumference, and are arranged in 6 equal intervals at the same distance from the center of the drive shaft (1) (in the present invention, the number of planetary gears (11) can be selected from 5 to 8). The detailed configuration of the planetary gears (11) will be described later.

The drive gear assembly (10) is sequentially installed with a first fixed plate (12a) and a first rotary plate (13a) on the right side with a planetary gear (11) in between, and with each support plate (15), a second fixed plate (12b) and a second rotary plate (13b) on the left side. For convenience of explanation, the direction in which the fixed plate (12), the rotary plate (13) and the each support plate (15) face the planetary gear (11) is defined as the inside, and the opposite direction is defined as the outside.

FIG. 3 illustrates the first fixed plates (12a, 22a) installed on the driving shaft (1) and the driven shaft (2), respectively, and FIG. 3a illustrates the second fixed plates (12b, 22b) installed on the driving shaft (1) and the driven shaft (2), respectively, and the shapes of the circular plates are all as viewed from the left side as illustrated in FIG. 1.

The fixed plate (12) fixed to the drive shaft (1) is a circular plate with a through-hole in the center, and is provided with a connecting key (12_1) on the inner periphery so as to be fixedly connected to an axial groove (1_1) formed on the outer periphery of the drive shaft (1) and rotates integrally with the drive shaft (1). When viewed from the left side, the fixed plate (12) has six planetary gear guide slots (12a_2) formed at equal intervals, each having a curved shape that curves clockwise toward the center of the circular plate (the number can be selected from 5 to 8, similar to the number of planetary gears (11)). The right end (right pin (113)) of the corresponding planetary gear (11) is fixed to the planetary gear guide slot (12a_2) of the first fixed plate (12a), and the left end (left pin (112)) of the corresponding planetary gear (11) is fixed to the planetary gear guide slot (12b_2) of the second fixed plate (12b).

Additionally, a spring pressure adjustment guide gear (12a_3) is formed on one side of the planetary gear guide slot (12a_2) of the first fixed plate (12a). The function of the spring pressure adjustment guide gear (12a_3) will be described later.

FIG. 4 illustrates first and second rotary plates (13) installed on a driving shaft (1), wherein (a) is a plan view of the rotary plate (13) viewed from the inside to the outside, (b) is a cross-sectional view of the second rotary plate (13b) coupled with the rotary arm (14), (c) is a conceptual view of the second sleeve (41b), (d) is a cross-sectional view of the sleeve (41) coupled to the driving shaft (1), (e) is a conceptual view of the first sleeve (41a), and (f) is a cross-sectional view of the first rotary plate (13a) coupled with the rotary arm (14).

In the drive gear assembly (10), the first and second rotary plates (13a, 13b) are installed on the outer side of the corresponding first and second fixed plates (12a, 12b) in the shape of discs, respectively. A cylinder having a screw (13_1) formed on the inner periphery is integrally formed at the center of the rotary plate (13), and is screw-connected to the outer periphery of a sleeve (41) coupled to a groove (1_1) of the drive shaft (1) by a coupling key (41_1), thereby restraining the rotation of the drive shaft (1) like the fixed plate (12).

In addition, the sleeve (41) is coupled to the groove (1_1) of the drive shaft (1) by the coupling key (41_1) and is constrained to the rotation of the drive shaft (1) but slides back and forth in the axial direction. The rotary plate (13) screw-coupled with the sleeve (41) rotates within a certain range in the clockwise or counterclockwise direction while maintaining a constant position relative to the fixed plate (12) in response to the reciprocating motion of the sleeve (41).

Figure 5 shows the change in the rotating arm according to the change in the rotation radius in a state where the rotating arm (14) is arranged and coupled to the rotating plate (13).

Referring to Fig. 5, six rotary arms (14) are arranged on each of the first and second rotary plates (13a, 13b), and one end of the rotary arms (14) is hingedly connected to the periphery of the first and second rotary plates (13a, 13b) at equal intervals. The other end of the rotary arms (14) is hingedly connected to the end (left pin (112) or right pin (113)) of a planetary gear (11) whose movement is constrained by a corresponding planetary gear guide slot (12_2) of a corresponding fixed plate (12). That is, the other end of the rotary arm (14) whose one end is hinged to the first rotary plate (13a) is hinged to the right end (right pin (113)) of the corresponding planetary gear (11), and the other end of the rotary arm (14) whose one end is hinged to the second rotary plate (13b) is hinged to the left end (left pin (112)) of the corresponding planetary gear (11).

Referring to FIG. 5, it is preferable that one end and the other end of the rotary arm (14) are bent toward the center of the rotary plate (13), and according to FIGS. 4 and 4a, it is preferable that one end (14_1) of the rotary arm (14) operates on a plane outside the rotary plate (13), and the other end (14_2) operates on a plane inside the rotary plate (13). Therefore, as shown in FIGS. 4 and 4a, the rotary arm (14) is preferably formed with a two-stage bend at one end (14_1) and the other end (14_2) so that it can rotate on two planes, and a rotary arm penetration groove (13_2) is preferably formed on the periphery of the rotary plate (13) so that the rotary arm (14) can pass through.

Referring to Fig. 6, each support plate (15) is a circular plate installed on the inner side of the second fixed plate (12b), and has a plurality of normal slots (15_1) formed at equal intervals in the normal direction. Each support plate (15) is not fixedly connected to the drive shaft (1). The normal slots (15_1) of each support plate (15) bind the engaging projections (112_1) provided on the outer periphery of the left pin (112) of the planetary gear (11), so that even if the planetary gear (11) moves closer to or farther away from the drive shaft (1), the direction of the planetary gear (11) is maintained constant with respect to the normal direction.

The driven gear assembly (20), like the driving gear assembly (10), has a first fixed plate (22a) and a first rotating plate (23a) on the right side with a planetary gear (21) in between, and a support plate (25), a second fixed plate (22b), and a second rotating plate (23b) are sequentially installed on the left side. The planetary gear (21), the first fixed plate (22a), the second fixed plate (22b), the first rotating plate (23a), the second rotating plate (23b), and the support plate (25) constituting the driven gear assembly (20) are substantially the same as the planetary gear (11), the first fixed plate (12a), the second fixed plate (12b), the first rotating plate (13a), the second rotating plate (13b), and the support plate (15) constituting the driving gear assembly (10), respectively.

However, since the rotation direction of the rotary plate (23) relative to the fixed plate (22) in the driven gear assembly (20) is opposite to the rotation direction of the rotary plate (13) relative to the fixed plate (12) in the drive gear assembly (10), the screw (23_1) for coupling the rotary plate (23) with the sleeve (41) in FIG. 4b is formed in the opposite direction to the screw (13_1) for coupling the rotary plate (13) with the sleeve (41) in FIG. 4. In addition, the spring pressure adjustment guide gear (22a_3) formed in the planetary gear guide slot (22a_2) of the first fixed plate (22a) in the driven gear assembly (20) in FIG. 3 is formed in the opposite direction to the spring pressure adjustment guide gear (12a_3) formed in the planetary gear guide slot (12a_2) of the first fixed plate (12a) in the drive gear assembly (10).

The drive gear assembly (10b) constituting the second embodiment of the belt-type gear transmission according to the present invention includes a planetary gear (11b) different from the planetary gear (11) included in the drive gear assembly (10) constituting the first embodiment of the belt-type gear transmission according to the present invention, and the driven gear assembly (20b) constituting the second embodiment of the belt-type gear transmission according to the present invention includes a planetary gear (21b) different from the planetary gear (21) included in the driven gear assembly (20) constituting the first embodiment of the belt-type gear transmission according to the present invention, and all other components are identical.

Referring to FIG. 7, in the present invention, the belt (30) is composed of a plurality of gear pieces (31) that are joined to a plurality of twisted steel wires (32) by tension bolts (33).

A retaining plate (34) is installed between the gear piece (31) and the twisted steel wire (32). The retaining plate (34) is provided with a number of steel wire receiving grooves (34_1) having a pattern similar to the twist of the twisted steel wire (32) to prevent slipping, and is provided with a slot-shaped bolt hole (34_2).

A retaining plate (34) is installed on a gear piece (31), and a twisted steel wire (32) is installed in a steel wire receiving groove (34_1) of the retaining plate. Then, a plate (35) is installed, and by repeatedly tightening all of these with tension bolts (33), a plurality of gear pieces (31) are combined with a plurality of twisted steel wires (32) to manufacture a belt (30).

In a preferred embodiment of the present invention, the gears provided on the belt (30) are not formed parallel to the axial direction, but are formed at an angle (20° to 40°, preferably 35°) from the axial direction. The function of the inclined gears formed on the belt (30) will be described in detail in the description of the planetary gear (11).

Referring again to FIGS. 1a and 1b, the transmission controller (40, 40b) of the present invention is configured to include first to fourth sleeves (41a, 41b, 41c, 41d), a linkage control unit (43, 43b), and a hydraulic device (44).

The first sleeve (41a) and the second sleeve (41b) are installed on the driving shaft (1) and slide back and forth in the axial direction while rotating together with the driving shaft (1), and the third sleeve (41c) and the fourth sleeve (41d) are installed on the driven shaft (2) and slide back and forth in the axial direction while rotating together with the driven shaft (2). As shown in FIGS. 4 and 4A, the first to fourth sleeves (41a, 41b, 41c, 41d) all have screws formed on their outer peripheries, and the screws formed on the first sleeve (41a) and the second sleeve (41b) and the screws formed on the third sleeve (41c) and the fourth sleeve (41d) are in opposite directions.

The linkage control unit (43, 43b) has an overall H shape, and is connected to the first to fourth sleeves (41a, 41b, 41c, 41d) and bearings (42) at each of the four corners, so that the first to fourth sleeves (41a, 41b, 41c, 41d) are connected and reciprocate on the corresponding shaft (drive shaft (1) or driven shaft (2)).

The hydraulic device (44) is equipped with a piston (45) to control the linkage control unit (43, 43b) to reciprocate in the axial direction.

The operation process of the gear controller (40, 40b) is as follows.

The hydraulic device (44) moves the linkage control member (43, 43b) axially (i.e., in the direction parallel to the driving shaft (1) and the driven shaft (2)) by the piston (45). When the linkage control member (43, 43b) moves axially, the first to fourth sleeves (41a, 41b, 41c, 41d) constrained by bearings (42) at the four corners of the linkage control member (43, 43b) move along the grooves (1_1, 2_1) installed on the corresponding shafts, respectively. At this time, the rotary plate (13, 23) screw-connected with the sleeve (41) cannot move together with the sleeve (41) from the installed position, but rotates relatively with respect to the fixed plate (12, 22). Since both ends of the planetary gears (11, 21, 11b, 21b) are hingedly connected to the rotating plate (13, 23) by the rotating arm (14, 24), the rotation of the rotating plate (13, 23) moves the planetary gears (11, 21, 11b, 21b), whose movement path is restricted by the planetary gear guide slots (12_2, 22_2) of the fixed plate (12, 22), to the center or periphery of the shaft (the driving shaft (1) or the driven shaft (2)), thereby changing the rotation radius of the driving gear assembly (10, 10b) and the driven gear assembly (20, 20b).

Figure 8a illustrates a comparison of the driving states of a belt-type gear transmission (first embodiment) according to the present invention, where (a) is when the rotation speed is reduced, and (b) is when the rotation speed is increased.

First, when reducing the rotational speed as shown in (a) of Fig. 8a, when the rotary plate (13a, 13b) of the driving shaft (1) rotates clockwise with respect to the fixed plate (12a, 12b), the planetary gear (11) hinge-constrained to the rotary arm (14) hinge-constrained to the rotary plate (13a, 13b) moves along the planetary gear guide slot (12_2, 22_2) of the fixed plate (12, 22), and the distance between the position of the planetary gear (11) and the driving shaft (1) becomes closer, thereby reducing the rotational radius.

In addition, the rotary plate (23a, 23b) provided on the driven shaft (2) rotates counterclockwise with respect to the fixed plate (22a, 22b), thereby increasing the distance between the position of the planetary gear (21) hinge-constrained to the rotary arm (24) hinge-constrained to the rotary plate (23a, 23b) and the driven shaft (2), thereby increasing the radius of rotation. In this state, the belt (30) transmits rotational force by connecting the planetary gears (11, 21) of the two shafts (the driving shaft (1) and the driven shaft (2)), thereby decreasing the rotational speed.

Meanwhile, when increasing the rotation speed, when the rotary plate (13a, 13b) of the drive shaft (1) rotates counterclockwise with respect to the fixed plate (12a, 12b), the planetary gear (11) hinge-constrained to the rotary arm (14) hinge-constrained to the rotary plate (13a, 13b) moves along the planetary gear guide slot (12_2, 22_2) of the fixed plate (12, 22), and the distance between the position of the planetary gear (11) and the drive shaft (1) increases, so that the rotation radius increases.

In addition, the rotary plate (23a, 23b) provided on the driven shaft (2) rotates clockwise with respect to the fixed plate (22a, 22b), thereby bringing the position of the planetary gear (21) hinge-constrained to the rotary arm (24) hinge-constrained to the rotary plate (23a, 23b) closer to the driven shaft (2), thereby reducing the radius of rotation. In this state, the belt (30) transmits rotational force by connecting the planetary gears (11, 21) of the two shafts (the driving shaft (1) and the driven shaft (2)), thereby increasing the rotational speed.

Figure 8b illustrates a comparison of the driving states of a belt-type gear transmission (second embodiment) according to the present invention, where (a) is when the rotation speed is reduced, and (b) is when the rotation speed is increased.

The operation content of Fig. 8b is the same as that of Fig. 8a.

Referring to FIGS. 9a and 9b, the transmission controller (40) according to the first embodiment of the present invention further includes a pressure position adjuster (46) that adjusts the pressure position on the linkage control unit (43) to reduce side effects due to eccentricity caused by the difference in the rotational radius of the drive gear assembly (10) and the driven gear assembly (20).

The pressure position adjuster (46) is equipped with a guide gear (46_1), a control rod (46_2), and a roller groove (46_3).

The guide gear (46_1) is installed in a straight line in a direction perpendicular to the drive shaft (1).

The control rod (46_2) is screw-connected with the piston (45) and rotates in response to the linear reciprocating motion of the piston (45), and a gear provided on the outer periphery is engaged with the guide gear (46_1) and moves in a direction perpendicular to the drive shaft (1) on the guide gear (46_1).

The roller home (46_3) is fixedly connected to the piston (45), and restrains the linkage control unit (43) in the axial direction and maintains it movable in the direction perpendicular to the axis.

Accordingly, when the piston (45) of the hydraulic device (44) moves in the axial direction, the control rod (46_2) screwed onto the piston (45) rotates on the guide gear (46_1) as the gear provided on the outer periphery engages with the guide gear (46_1). As the control rod (46_2) moves, the hydraulic device (44) and the piston (45) also move in a direction perpendicular to the axis. At this time, the roller groove (46_3) controls the linkage control member (43) to reciprocate in the axial direction while maintaining the piston (45) to move freely in the direction perpendicular to the axis.

Referring to FIGS. 9c to 9b_1, the transmission controller (40b) according to the second embodiment of the present invention includes a pressure position adjuster (46b) having a different configuration from the pressure position adjuster (46) included in the transmission controller (40) according to the first embodiment of the present invention.

The pressure position adjuster (46b) is provided with a guide gear (46b_1), a control rod (46b_2), a rotation gear (46b_3), a rotation arm (46b_4), a rotation restraint pin (46b_7), and a linkage control restraint pin (46b_5), and the linkage control (43b) is provided with a guide slot (43b_3) formed in a direction perpendicular to the driving shaft.

The guide gear (46b_1) is installed in a straight line in a direction parallel to the driving shaft (1).

One end of the control rod (46b_2) is fixedly connected to the piston (45) of the hydraulic device (44), and the other end is hinge-connected to the rotary gear (46b_3) and the rotary arm (46b_4) by a rotary restraint pin (46b_7), and moves axially back and forth along the piston (45).

A key (46b_8) is provided on the rotation restraint pin (46b_7), and one end of the rotation gear (46b_3) and the rotation arm (46b_4) are restrained together by the key (46b_8) of the rotation restraint pin (46b_7), so that the rotation arm (46b_4) also rotates around the rotation restraint pin (46b_7) as the rotation gear (46b_3) rotates.

The gear of the rotary gear (46b_3) meshes with the gear of the guide gear (46b_1) and rotates as the control rod (46b_2) reciprocates.

One end of the rotary arm (46b_4) is constrained to the rotary gear (46b_3) by the rotary constraining pin (46b_7), but the other end is constrained to the guide slot (43b_3) of the linkage control unit (43b) by the linkage control unit constraining pin (46b_5), so that the linkage control unit (43b) moves freely in the vertical direction of the axial direction while being controlled to reciprocate in the axial direction.

Ultimately, the pressurized position adjuster (46, 46b) according to the present invention can reduce side effects due to eccentricity caused by a difference in the rotational radius by controlling the hydraulic device (44) to move toward the drive gear assembly (10, 10b) and the driven gear assembly (20, 20b) with a relatively larger rotational radius to pressurize the linkage control unit (43, 43b).

Referring to FIGS. 10a and 10b, the transmission controller (40) according to the first embodiment of the present invention further includes a roller device (48) that corrects a belt length difference caused by a difference in the rotational radius of the drive gear assembly (10) and the driven gear assembly (20).

The roller device (48) has first and second supports (48_1), first and second roller arms (48_2), a roller (48_3), and first and second linkage control arms (43_1).

The first and second supports (48_1) are installed at a certain distance above and below the belt (30) connected between the drive gear assembly (10) and the driven gear assembly (20).

The first and second roller arms (48_2) are hingedly connected to the first and second supports (48_1), respectively, and rotate by an inclined gear (48_4) provided at one end while pressing the belt (30) by a roller (48_3) provided at the other end.

The first and second linkage control arms (43_1) are each fixedly connected to the linkage control arm (43) at one end and equipped with an inclined gear (43_2) at the other end.

When the linkage control unit (43) is moved linearly by the piston (45) of the hydraulic device (44), the first and second linkage control arms (43_1) fixedly connected to the linkage control unit (43) also move linearly together with the linkage control unit (43). Accordingly, the first and second roller arms (48_2) are rotated within a certain range by the inclined gears (43_2) provided on the first and second linkage control arms (43_1) and the inclined gears (48_4) provided on the first and second roller arms (48_2). At this time, the first and second roller arms (48_2) rotate toward the smaller rotation radius of the driving gear assembly (10) and the driven gear assembly (20), respectively, to pressurize the belt (30). By appropriately adjusting the rotation radius and rotation range of the first and second roller arms (48_2), the belt length difference caused by the difference in the rotation radius of the driving gear assembly (10) and the driven gear assembly (20) is reduced to within the allowable range.

Referring to FIGS. 10c and 10d, the transmission controller (40b) according to the second embodiment of the present invention further includes a roller device (48b) that corrects a difference in belt length caused by a difference in the rotational radius of the drive gear assembly (10b) and the driven gear assembly (20b).

The roller device (48b) includes first and second support members (48b_1), first and second roller arms (48b_2), a roller (48b_3), first and second linkage control arms (43b_1), and first and second roller hinge extension rods (48b_5).

The first and second supports (48b_1) are installed at a certain distance above and below the belt (30) connected between the driving gear assembly (10b) and the driven gear assembly (20b).

The first and second linkage control arms (43b_1) are each fixedly connected to the linkage control arm (43b) at one end, and are provided with an inclined gear (43b_2) at the other end.

The first and second roller hinge extension bars (48b_5) each have an inclined gear (48b_4) at one end that meshes with the inclined gear (43b_2) of the first and second linkage control arms (43b_1), and the other end is fixedly connected to one end of the first and second roller arms (48b_2).

The first and second roller arms (48b_2) are hinge-connected to the first and second supports (48b_1), respectively, and rotate by the first and second roller hinge extension rods (48b_5) connected to one end while pressing the belt (30) by the roller (48b_3) provided at the other end.

When the linkage control unit (43b) moves in a straight line, the first and second linkage control arm arms (43b_1) fixedly connected to the linkage control unit (43b) also move in a straight line, and accordingly, the first and second roller hinge extension rods (48b_5) gear-coupled by the inclined gear (43b_2) provided on the first and second linkage control arm arms (43b_1) and the inclined gear (48b_4) provided therein rotate.

As the first and second roller hinge extension rods (48b_5) rotate, the first and second roller arms (48b_2) keyed to the first and second roller hinge extension rods (48b_5) rotate within a certain range.

At this time, the first and second roller arms (48b_2) rotate toward the one with the smaller rotation radius among the driving gear assembly (10b) and the driven gear assembly (20b), respectively, to pressurize the belt (30). By appropriately adjusting the rotation radius and rotation range of the first and second roller arms (48b_2), the difference in length of the belt (30) caused by the difference in the rotation radius of the driving gear assembly (10b) and the driven gear assembly (20b) is reduced to within the allowable range.

Referring to FIG. 11a, the planetary gear (11, 21) according to the first embodiment of the present invention is configured to include a main body (110), a gear sleeve (120), a two-way buffer (130), a spring pressure regulator (140), and a rotation inducer (150).

The main body (110) of the planetary gear (11) includes an inner sleeve (111) ((a) of FIG. 12a), a left pin (112) ((b) of FIG. 12a) located on the left side of the inner sleeve (111), and a right pin (113) ((c) of FIG. 12a) located on the right side of the inner sleeve (111).

My sleeve (111) has a cylindrical shape and accommodates a two-way buffer (130) inside.

The left pin (112) is hinge-coupled to a rotary arm (14) hinge-coupled to a second rotary plate (13b) and moves while being restrained in the planetary gear guide slot (12_2) of the second fixed plate (12b) according to the rotation of the second rotary plate (13b). At this time, the engaging projection (112_1) provided on the left pin (112) is restrained by the normal slot (15_1) of the rotary plate (15), so that other components coupled with the left pin (112) can also maintain a constant angle with the normal line determined by the normal slot (15_1).

In contrast, one end of the right pin (113) is hingedly connected to a rotary arm (14) hingedly connected to the first rotary plate (13a). A spring pressure adjustment gear (113_1) is formed on the outer periphery of the other end of the right pin (113), so that when the first rotary plate (13a) rotates, it engages with the spring pressure adjustment guide gear (12_3) formed in the planetary gear guide slot (12_2) of the first fixed plate (12a) and rotates while being restrained by the planetary gear guide slot (12_2).

The gear sleeve (120) of the planetary gear (11) includes an outer sleeve (121) ((a) of Fig. 12b), a left fixing screw (122) ((b) of Fig. 12b), and a right fixing screw (123) ((c) of Fig. 12b).

The outer sleeve (121) is in the form of a cylinder that wraps around a part of the main body (110), and is capable of moving left and right around the periphery of the main body (110), is coupled to be rotatable within a small range, and is formed with a gear (121_1) that maintains an inclination of a constant angle (θ) with respect to the axial direction while meshing with the gear of the belt (30) on at least a part of the outer periphery. Here, θ is 20° to 40°, and is preferably maintained at approximately 35°.

The gears (121_1) provided in the gear sleeve (120) and the gears provided in the belt (30) form a curved surface, and the radius of the curved surface of the gears is made more than twice as large as the radius of the gear sleeve (120), thereby smoothing the microscopic rotation of the gear sleeve (120) during gear shifting.

The left fixing screw (122) and the right fixing screw (123) are each fixed by screw connection at both ends of the inner circumference of the outer sleeve (121), so as to easily accommodate other configurations inside. The left fixing screw (122) and the right fixing screw (123) have the function of transmitting the pressure according to the left and right movement of the gear sleeve (120) to other configurations (left support plate (132), rotation auxiliary ring (161) (Fig. 12f)).

The two-way shock absorber (130) of the planetary gear (11) is configured to include a main spring (131) ((a) of FIG. 12c), a left support plate (132) ((b) of FIG. 12c), and a right support plate (133) ((c) of FIG. 12c), and buffers the left-right movement of the gear sleeve (120) and limits it within a certain range.

The left support plate (132) is supported on the left by the left pin (112) and cannot move any further, but is pressed on the right by the left fixing screw (122) and can move within a certain range (approximately 1/2 pitch) while pressing the main spring (131) within the inner sleeve (111).

The right support plate (133) is supported on the right by a compression rod (141) to be described below and cannot move any further, but on the left, it is pressed by the compression rod (141) and can move within a certain range (approximately 1/2 pitch) while pressing the main spring (131) within the inner sleeve (111).

The spring pressure regulator (140) of the planetary gear (11) includes a compression rod (141) ((a) of FIG. 12d) and a pressure regulating pin (142) ((b) of FIG. 12d), and reduces the pressure of the main spring (131) when the rotation radius is large with respect to the driving shaft (1), and increases the pressure of the main spring (131) when the rotation radius is small.

The compression rod (141) is a cylinder-shaped rod with a screw formed on the inner surface, and is screw-connected to the other end of the pressure regulating pin (142). As the pressure regulating pin (142) rotates, the compression rod (141) does not rotate but reciprocates in a straight line in the longitudinal direction to support the right support plate (133).

One end of the pressure regulating pin (142) is integrally connected to the right pin (113) and rotates together with the right pin (113). In addition, the other end of the pressure regulating pin (142) has a screw formed on the outer periphery and is screw-connected with the inner periphery of the compression rod (141). An adjusting projection (142_1) is formed on the outer periphery between one end and the other end of the pressure regulating pin (142), and the leftward movement pressure of the gear sleeve (120) is transmitted from the right fixing screw (123) to the adjusting projection (142_1) through the rotation auxiliary ring (161) (Fig. 12f) to move the pressure regulating pin (142) to the left.

The rotation inducer (150) of the planetary gear (11) includes an auxiliary spring (151) ((c) of FIG. 12e), a left rotation pressure ring (152) ((a) of FIG. 12e), a left support ring (153) ((b) of FIG. 12e), a right support ring (154) ((d) of FIG. 12e), and a right rotation pressure ring (155) ((e) of FIG. 12e), and induces the gear sleeve (120) to rotate in a fine range in response to the left and right movement pressure of the gear sleeve (120), and provides auxiliary buffering for the left and right movement of the gear sleeve (120).

The left-hand rotation pressure ring (152) is coupled to the gear sleeve (120) and rotates synchronously, and has one end that receives rightward movement pressure from the gear sleeve (120) and the other end that has a side inclined groove (152_1) formed therein.

The left support ring (153) is located on the left side of the auxiliary spring (151) and is installed so that it can move only to the right from the compression rod (141). At one end, a side slope key (153_1) corresponding to the side slope groove (152_1) of the left rotation pressure ring (152) is formed, and at the other end, the auxiliary spring (151) is supported.

The right-hand rotation pressure ring (155) is coupled to the gear sleeve (120) and rotates synchronously, and has one end that receives leftward movement pressure from the gear sleeve (120) and the other end that has a side inclined groove (155_1) formed therein.

The right support ring (155) is located on the right side of the auxiliary spring (151) and is installed so that it can move only to the left from the compression rod (141). At one end, a side slope key (154_1) corresponding to the side slope groove (155_1) of the right rotation pressure ring (155) is formed, and at the other end, the auxiliary spring (151) is supported.

The left rotation pressure ring (152) and the right rotation pressure ring (154) of the rotation inducer (150) rotate in opposite directions within a minute range in response to the movement pressure from the gear sleeve (120), thereby rotating the gear sleeve (120) that is synchronized with the rotation.

In the case of the planetary gear (11) according to the present invention, a rotation auxiliary ring (161) (Fig. 12f) having an inner key (161_2) in a ring shape at one end and an outer key (161_1) formed clockwise with a keyway slope offset by about 2/3 of the inner key (161_2) is installed between the right rotation pressure ring (154) and the right fixing screw (123). The outer key (161_1) of the rotation auxiliary ring (161) is engaged with a groove provided in the right rotation pressure ring (154), and the inner key (161_2) is engaged with a groove provided in the adjustment projection (142_1) of the pressure control pin (142) by about 1/3 of the way. When the other end of the rotation auxiliary ring (161) is pressed against the right fixing screw (123), the inner key (161_2) engages with the key of the pressure control pin (142) and partially rotates, and the outer key (161_1) first presses the right rotation pressure ring (154), thereby supporting the rotation of the gear sleeve (120).

According to the present invention, when the gear (121_1) provided on the planetary gear (11) encounters the gear (30_1) provided on the belt (30), the gear teeth do not mesh with the gear grooves during the gear shifting process, but the gear teeth encounter each other. This situation can cause serious damage to both the planetary gear (11) and the belt (30). Therefore, in a preferred embodiment of the present invention, both the gear (121_1) provided on the planetary gear (11) and the gear (30_1) provided on the belt (30) are not formed parallel to the axial direction, but are formed at an angle (20° to 40°, preferably 35°) in the axial direction, so that the gear (121_1) provided on the planetary gear (11) moves 1/2 pitch in the axial direction from the gear provided on the belt (30) so that the gear teeth and gear grooves of both gears mesh.

Hereinafter, the operation process of the bidirectional shock absorber (130) of the planetary gear (11) according to the present invention will be described in detail. The bidirectional shock absorber (130) moves the gear sleeve (120) left and right with respect to the main body (110) so that the gear (121_1) provided on the planetary gear (11) meshes with the gear (30_1) provided on the belt (30).

When the gear (30_1) provided on the belt (30) meshes with the gear (121_1) provided on the planetary gear (11) in the forward direction of rotation (see (a) of FIG. 13), the planetary gear (11) is pushed to the left in the direction of rotation of the belt (30) by the generated axial force, and the right fixing screw (123) coupled to the outer sleeve (121) presses the rotation auxiliary ring (161) (see (c) of FIG. 13). Accordingly, the gear provided on the rotation auxiliary ring (161) partially rotates and pressurizes the gear provided on the adjusting projection (142_1) of the pressure regulating pin (142) that is in a partially engaged state, and the pressure regulating pin (142) pressurizes the main spring (131) by the screw-coupled compression rod (141) and the right support plate (133). At this time, the main spring (131) is supported on the left support plate (131) which is supported on the left pin (112) of the planetary gear (11) which is supported on the second fixed plate (12b). Therefore, the leftward movement of the gear sleeve (120) in the planetary gear (11) is limited within a certain range (see (d) of FIG. 13).

When the gear (30_1) provided on the belt (30) meshes with the gear (121_1) provided on the planetary gear (11) at the rear in the rotational direction (see (a) of FIG. 13a), the planetary gear (11) is pushed to the right in the rotational direction of the belt (30), and the left fixing screw (122) coupled to the outer sleeve (121) presses the left support plate (132) (see (c) of FIG. 13a), and the left support plate (132) presses the main spring (131). At this time, the compression rod (141) screw-connected with the pressure regulating pin (142) supported on the first fixing plate (12a) supports the main spring (131) with the right support plate (133). Therefore, the rightward movement of the gear sleeve (120) in the planetary gear (11) is limited within a certain range (see (d) of Fig. 13a).

Hereinafter, the operation process of the rotation inducer (150) of the planetary gear (11) according to the present invention will be described in detail. The rotation inducer (15) is an auxiliary device that facilitates movement left and right with respect to the main body (110) by rotating the gear sleeve (120) in a minute range with respect to the main body (110) in a section adjacent to a specific point where the gear (121_1) of the planetary gear (11) is excessively misaligned with the gear (30_1) provided on the belt (30) when meshing with each other.

When the gear provided on the belt (30) meshes with the gear (121_1) provided on the planetary gear (11) in the forward direction of rotation (see (a) of FIG. 13), the right rotation pressure ring (155) rotates synchronously with the outer sleeve (121) by having the keys provided on the outer periphery fixed to the grooves provided on the inner periphery of the outer sleeve (121). The right fixing screw (123) supports the rotation auxiliary ring (161), and the outer key (161_1) provided on the rotation auxiliary ring (161) is engaged with the groove provided on the right rotation pressure ring (155). In addition, one end of the right rotation pressure ring (155) is provided with a side inclined groove (155_1) and is in one-way sliding contact with the side inclined key (154_1) provided on one end of the right support ring (154). Accordingly, when the right rotation pressure ring (155) presses the right support ring (154) in the opposing direction, they rotate each other within a minute range. At this time, the key provided on the inner periphery of the right support ring (154) is restrained from rotating by being fixed to the groove provided on the outer periphery of the compression rod (141), and the compression rod (141) is coupled in a state where it does not rotate with respect to the inner sleeve (111), so that the outer sleeve (121), which rotates synchronously with the right rotation pressure ring (155) by the pressure of the right fixing screw (123), rotates minutely with respect to the main body (110) (see (b) of FIG. 13). The right support ring (154), whose rotation is restrained, pressurizes the auxiliary spring (151) while moving to the left.

Meanwhile, when the gear provided on the belt (30) meshes with the gear provided on the planetary gear (11) at the rear in the rotational direction (see (a) of FIG. 13a), the left rotation pressure ring (152) rotates synchronously with the outer sleeve (121) by having a key provided on the outer periphery thereof bound to a groove provided on the inner periphery of the outer sleeve (121). One end of the left rotation pressure ring (152) is supported by the end of the groove provided on the outer sleeve (121). One end of the left rotation pressure ring (152) is provided with a side inclined groove (152_1) and comes into one-way sliding contact with a side inclined key (153_1) provided on one end of the left support ring (153). Therefore, when the left rotation pressure ring (152) presses the left support ring (153) in the opposite direction, rotation occurs between them within a minute range.

At this time, the key provided on the inner periphery of the left support ring (153) is restrained from rotation by being fixed to the groove provided on the outer periphery of the compression rod (141). Since the compression rod (141) is coupled in a state of not rotating with respect to the inner sleeve (111), the outer sleeve (121) which rotates synchronously with the left rotation pressure ring (152) by the pressure of the left fixing screw (122) rotates slightly with respect to the main body (110) (see (b) of FIG. 13a). The left support ring (153) which is restrained from rotating pressurizes the auxiliary spring (151) while moving to the right.

In summary, when the operation process of the two-way buffer (130) and the rotation inducer (150) is engaged in the forward direction of the rotation of the gear (121_1) provided on the planetary gear (11), as shown in (b) of FIG. 13, the gear sleeve (120) of the planetary gear (11) rotates slightly to the boundary between the curved portion formed on the gear teeth and the gear slope toward the rear of the rotation direction of the gear (121_1) and moves to reach the gear slope, and then, as shown in (d) of FIG. 13, the gear sleeve (120) of the planetary gear (11) moves further to the left to the gear groove, so that the two gears are completely engaged.

Meanwhile, when the gear (30_1) provided on the belt (30) meshes with the gear (121_1) provided on the planetary gear (11) at the rear in the rotational direction, as shown in (b) of FIG. 13a, the gear sleeve (120) of the planetary gear (11) rotates slightly toward the front in the rotational direction of the gear (121_1) to the boundary between the curved portion formed on the gear teeth and the gear slope, and then moves to reach the gear slope, and as shown in (d) of FIG. 10c, the gear sleeve (120) of the planetary gear (11) moves further to the right to the gear groove, so that the two gears are completely meshed.

Hereinafter, the operation process of the spring pressure regulator (140) of the planetary gear (11) according to the present invention will be described in detail.

The main spring (131) provided in the two-way shock absorber (130) needs to reduce the spring pressure (see (a) of FIG. 14) when the torque is low (i.e., the rotation radius is large) with respect to the drive shaft (1) and increase the spring pressure (see (b) of FIG. 14) when the torque is high (i.e., the rotation radius is small). The spring pressure regulator (140) automatically detects the position of the planetary gear (11) and automatically adjusts the spring pressure according to the size of the drive shaft rotation radius.

In the planetary gear guide slot (12_2) of the first fixed plate (12a) of the drive gear assembly (10), a spring pressure adjustment guide gear (12_3) is formed, and meshes with a spring pressure adjustment gear (113_1) formed on the outer periphery of the right pin (113) of the planetary gear (11). Therefore, as the planetary gear (11) moves along the planetary gear guide slot (12_2), the right pin (113) rotates. A key formed on one end of the pressure adjustment pin (142) is engaged with a groove formed on the inner periphery of the right pin (113), so that the pressure adjustment pin (142) rotates together with the right pin (113). A screw is formed on the outer periphery of the other end of the pressure adjustment pin (142) and is screw-connected with the inner periphery of the compression rod (141). Accordingly, the compression rod (141) with limited rotation supports the right support plate (133) while making a linear reciprocating motion by the rotation of the pressure adjustment pin (142) to adjust the pressure of the main spring (131). At this time, the spring pressure adjustment guide gear (12a_3) provided on the first fixed plate (12a) of the driving gear assembly (10) is formed in the opposite direction to the spring pressure adjustment guide gear (22a_3) provided on the first fixed plate (22a) of the driven gear assembly (20), so that the planetary gear (11) of the driving gear assembly (10) and the planetary gear (21) of the driven gear assembly (20) can maintain the pressure of the main spring (131) to be the same.

Referring to FIG. 11b, the planetary gear (11b, 21b) according to the second embodiment of the present invention is configured to include a main body (110b), a gear sleeve (120b), a two-way buffer (130b), a spring pressure regulator (140b), and a rotation inducer (150b).

The main body (110b) of the planetary gear (11b) includes a left pin (112b) ((a) of Fig. 12g) and a right pin (113b) ((b) of Fig. 12g).

The left pin (112b) is hingedly connected to a rotary arm (14) hingedly connected to the second rotary plate (13b), and moves while being constrained to the planetary gear guide slot (12_2) of the second fixed plate (12b) according to the rotation of the second rotary plate (13b). At this time, the engaging projection (112b_1) provided on the left pin (112b) is constrained by the normal slot (15_1) of the rotary plate (15), so that other components coupled with the left pin (112b) can also maintain a constant angle with the normal line determined by the normal slot (15_1).

In contrast, one end of the right pin (113b) is hingedly connected to a rotary arm (14) that is hingedly connected to the first rotary plate (13a). A spring pressure adjustment gear (113_1) is formed on the outer periphery of the other end of the right pin (113b), so that when the first rotary plate (13a) rotates, the gear meshes with the spring pressure adjustment guide gear (12_3) formed in the planetary gear guide slot (12_2) of the first fixed plate (12a) and rotates while being restrained by the planetary gear guide slot (12_2).

The gear sleeve (120b) of the planetary gear (11b) includes an outer sleeve (121b) ((a) of FIG. 12h), a left fixing screw (122b) ((b) of FIG. 12h), and a right fixing screw (123b) ((c) of FIG. 12h).

The outer sleeve (121b), the left fixing screw (122b), and the right fixing screw (123b) constituting the gear sleeve (120b) according to the second embodiment of the present invention are identical in shape and function to the outer sleeve (121), the left fixing screw (122), and the right fixing screw (123) constituting the gear sleeve (120) according to the first embodiment of the present invention, respectively.

The two-way shock absorber (130b) of the planetary gear (11b) is configured to include a main spring (131b) ((a) of FIG. 12i), a left support plate (132b) ((b) of FIG. 12i), and a right support plate (133b) ((c) of FIG. 12i), and buffers the left-right movement of the gear sleeve (120b) and limits it within a certain range.

The main spring (131b) constituting the two-way shock absorber (130b) according to the second embodiment of the present invention can be implemented as a coil spring in a form that surrounds the left pin (112b) extended into the inside of the outer sleeve (121b), unlike the main spring (131) constituting the two-way shock absorber (130) according to the first embodiment of the present invention, which is accommodated inside the inner sleeve (111) (i.e., located between the inner diameter of the outer sleeve (121b) constituting the gear sleeve (120b) and the outer diameter of the left pin (112b).

The left support plate (132b) is supported on the left by the left pin (112b) and cannot move any further, but is pressed on the right by the left fixing screw (122b) and can move within a certain range (approximately 1/2 pitch) while pressing the main spring (131b) located on the outer periphery of the left pin (112b).

The right support plate (133b) is supported on the right by a compression rod (141b) to be described below and cannot move any further, but on the left, it is pressed by the compression rod (141b) and can move to a certain range (approximately 1/2 pitch) while pressing the main spring (131b) located on the outer periphery of the left pin (112b).

The spring pressure regulator (140b) of the planetary gear (11b) includes a compression rod (141b) ((a) of FIG. 12j) and a pressure regulating pin (142b) ((b) of FIG. 12j), and reduces the pressure of the main spring (131b) when the rotation radius is large with respect to the driving shaft (1), and increases the pressure of the main spring (131b) when the rotation radius is small.

The compression rod (141b) is a cylinder-shaped rod with a screw formed on its inner surface, and is screw-connected to the other end of the pressure regulating pin (142b). As the pressure regulating pin (142b) rotates, the compression rod (141b) does not rotate but reciprocates in a straight line in the longitudinal direction to support the right support plate (133b).

In the planetary gear (11b) according to the second embodiment of the present invention, the right support plate (133b) of the bidirectional buffer (130b) and the compression rod (141b) of the spring pressure regulator (140b) can be implemented in an integrated form.

One end of the pressure regulating pin (142b) is integrally connected to the right pin (113b) and rotates together with the right pin (113b). In addition, the other end of the pressure regulating pin (142b) has a screw formed on the outer periphery and is screw-connected with the inner periphery of the compression rod (141b). An adjusting projection (142b_1) is formed on the outer periphery between one end and the other end of the pressure regulating pin (142b), and the leftward movement pressure of the gear sleeve (120b) is transmitted from the right fixing screw (123b) to the adjusting projection (142b_1) through the rotation auxiliary ring (161b) (Fig. 12l) to move the pressure regulating pin (142b) to the left.

The rotation inducer (150b) of the planetary gear (11b) includes an auxiliary spring (151b) ((c) of FIG. 12k), a left rotation pressure ring (152b) ((a) of FIG. 12k), a left support ring (153b) ((b) of FIG. 12k), a right support ring (154b) ((d) of FIG. 12k), and a right rotation pressure ring (155b) ((e) of FIG. 12k), and induces the gear sleeve (120b) to rotate in a fine range in response to the left and right movement pressure of the gear sleeve (120b), and provides auxiliary buffering for the left and right movement of the gear sleeve (120b).

The left rotation pressure ring (152b) is coupled to the gear sleeve (120b) and rotates synchronously, and has one end that receives rightward movement pressure from the gear sleeve (120b) and the other end that has a side groove (152b_1) formed therein.

The left support ring (153b) is located on the left side of the auxiliary spring (151b) and is installed so as to be able to move only to the right from the right support plate (133b). A side key (153b_1) corresponding to the side groove (152b_1) of the left rotation pressure ring (152b) is formed at one end, and the other end supports the auxiliary spring (151b).

The right-hand rotation pressure ring (155b) is coupled to the gear sleeve (120b) and rotates synchronously, and has one end that receives leftward movement pressure from the gear sleeve (120) and the other end formed with a side groove (155/b_1).

The right support ring (155/b) is located on the right side of the auxiliary spring (151b) and is installed so as to be able to move only to the left. A side key (154b_1) corresponding to the side groove (155b_1) of the right rotation pressure ring (155b) is formed at one end, and the other end supports the auxiliary spring (151b).

The left rotation pressure ring (152b) and the right rotation pressure ring (154b) of the rotation inducer (150b) rotate in opposite directions within a minute range in response to the movement pressure from the gear sleeve (120b), thereby rotating the gear sleeve (120b) that is synchronized with the rotation.

The rotation auxiliary ring (161b) according to the second embodiment of the present invention has the same shape and function as the rotation auxiliary ring (161) according to the first embodiment of the present invention.

The present invention has been described above, focusing on preferred embodiments thereof. Those skilled in the art will appreciate that the present invention can be implemented in modified forms without departing from its essential characteristics. Therefore, the disclosed embodiments should be considered illustrative rather than restrictive. The scope of the present invention is set forth in the claims, not the foregoing description, and all differences within the scope equivalent thereto should be construed as being encompassed by the present invention.

According to the present invention, the rotation radius of the planetary gear can be adjusted to easily change gears by controlling the rotation plates of the drive gear assembly of the drive shaft and the driven gear assembly of the driven shaft to rotate in conjunction with each other through a linear reciprocating motion in a direction parallel to the drive shaft by the piston of the hydraulic device.

In addition, according to the present invention, the problem of the length of the belt connecting the planetary gear of the drive shaft and the planetary gear of the driven shaft changing as the rotation radius of the planetary gear changes can be solved by a roller device installed above and below the belt and operating in conjunction with a linear reciprocating motion by a hydraulic device.

In addition, according to the present invention, an eccentric phenomenon occurring due to a difference in the rotational radius of the planetary gear in the driving shaft and the driven shaft can be resolved by adjusting the position at which the linkage control unit is pressed by a pressure position adjuster that operates in conjunction with the linear reciprocating motion by the hydraulic device.

Claims (10)

In a belt-type gear transmission that transmits the rotational power of the driving shaft to the driven shaft, A drive gear assembly installed on the above drive shaft; A driven gear assembly installed on the above driven shaft; A belt having a gear formed inside and connecting the drive gear assembly and the driven gear assembly to transmit the rotational force of the drive shaft to the driven shaft; and A belt-type gear transmission including a transmission controller that controls transmission so that an increase or decrease in the size of the rotation radius of the above-mentioned driving gear assembly is mutually linked with an increase or decrease in the size of the rotation radius of the above-mentioned driven gear assembly. In the first paragraph, the transmission controller First and second sleeves, each installed on the drive shaft and sliding reciprocally in an axial direction parallel to the drive shaft, and having screw threads formed on the outer periphery; Third and fourth sleeves, each installed on the driven shaft and sliding reciprocally in the axial direction, and having screw threads formed on the outer periphery; An H-shaped joint control unit connected by the first to fourth sleeves and bearings at each of the four corners; and A belt-type gear transmission characterized by including a hydraulic device having a piston that reciprocates the above-mentioned linkage control unit in the axial direction. In the second paragraph, A belt-type gear transmission, characterized in that the screw threads formed on the outer periphery of the first and second sleeves and the third and fourth sleeves are formed in opposite directions. In the second or third paragraph, A belt-type gear transmission characterized in that the hydraulic device further includes a pressure position adjuster that controls the drive gear assembly and the driven gear assembly to move toward the one with a relatively larger rotation radius to pressurize the linkage control unit. In the fourth paragraph, the pressure position adjuster, A guide gear installed in a direction perpendicular to the above axial direction; A control rod having a gear that engages with the guide gear on the outer periphery and is screw-connected with the piston and moves on the guide gear while rotating in response to the linear reciprocating motion of the piston; and A belt-type gear transmission characterized by including a roller groove fixedly connected to the piston and restraining the linkage control member in the axial direction and allowing movement in a direction perpendicular to the axial direction. In the second or third paragraph, First and second linkage control arm arms, each of which has one end fixedly connected to the linkage control arm and the other end equipped with an inclined gear; First and second supports installed on both sides between the driving gear assembly and the driven gear assembly; and It includes first and second roller arms, which are pin-connected to the first and second supports, respectively, and pressurize the belt by the roller while rotating by the inclined gear; A belt-type gear transmission characterized in that the linear reciprocating motion of the linkage control unit further includes a roller device in which the first and second roller arms rotate within a certain range by the inclined gears of the first and second roller arms corresponding to the inclined gears provided on the first and second linkage control unit arms. In paragraph 6, A belt-type gear transmission characterized in that the first and second roller arms rotate toward the smaller rotation radius of the drive gear assembly and the driven gear assembly, respectively, to pressurize the belt. In a belt-type gear transmission that transmits the rotational power of the driving shaft to the driven shaft, A drive gear assembly installed on the above drive shaft; A driven gear assembly installed on the above driven shaft; A belt having a gear formed inside and connecting the drive gear assembly and the driven gear assembly to transmit the rotational force of the drive shaft to the driven shaft; and A transmission controller that controls the transmission so that the increase or decrease in the size of the rotation radius of the above driving gear assembly is mutually linked with the increase or decrease in the size of the rotation radius of the above driven gear assembly; The above gear controller, First and second sleeves, each installed on the drive shaft and sliding reciprocally in an axial direction parallel to the drive shaft, and having screw threads formed on the outer periphery; Third and fourth sleeves, each installed on the driven shaft and sliding reciprocally in the axial direction, and having screw threads formed on the outer periphery; An H-shaped joint control unit connected by the first to fourth sleeves and bearings at each of the four corners; and A hydraulic device having a piston that reciprocates the above-mentioned linkage control unit in the axial direction; The screw threads formed on the outer periphery of the first and second sleeves and the third and fourth sleeves are formed in opposite directions, The above hydraulic device further includes a pressure position controller that controls the drive gear assembly and the driven gear assembly to move toward the one with a relatively larger rotation radius to pressurize the linkage control unit. The above pressure position adjuster is, A guide gear installed in a direction parallel to the above axial direction; A guide slot formed in a direction perpendicular to the axial direction on the above linkage control panel; First, a control rod that is fixedly connected to the piston and moves reciprocally in the axial direction; A rotary gear that is hinge-connected to the other end of the control rod by a rotary restraint pin and meshes with the guide gear; A belt-type gear transmission characterized by including a rotary arm, one end of which is hinge-connected to the other end of the control rod by the rotary restraint pin and is rotated by being restrained by the rotation of the rotary gear by the key of the rotary restraint pin, and the other end of which is restrained in the axial direction by a guide slot and is maintained movable in a direction perpendicular to the axial direction. In paragraph 8, First and second linkage control arm arms, each of which has one end fixedly connected to the linkage control arm and the other end equipped with an inclined gear; First and second supports installed on both sides between the driving gear assembly and the driven gear assembly; First and second roller hinge extension rods each having an inclined gear meshed with the inclined gears of the first and second linkage control arms; and It includes first and second roller arms, which are hinge-connected to the first and second supports, respectively, and rotate by an inclined gear installed by extending by first and second roller hinge extension rods connected to one end thereof while pressing a belt by a roller provided at the other end; A belt-type gear transmission characterized in that the linear reciprocating motion of the above-mentioned linkage control unit further includes a roller device in which the first and second roller arms rotate within a certain range by the inclined gears of the first and second roller hinge extension rods corresponding to the inclined gears provided on the first and second linkage control unit arms. In paragraph 9, A belt-type gear transmission characterized in that the first and second roller arms rotate toward the smaller rotation radius of the drive gear assembly and the driven gear assembly, respectively, to pressurize the belt.