Belt-type gear transmission controlling the driving side and driven side in conjunction with each other

Abstract

The present invention relates to a belt-type gear transmission that controls the drive side and the driven side in conjunction to control the rotational radius of the drive gear assembly of the drive shaft and the driven gear assembly of the driven shaft by linear reciprocating motion in a direction parallel to the drive shaft by a piston of a hydraulic device. The belt-type gear transmission according to the present invention, which transmits the rotational force of the drive shaft to the driven shaft, comprises: a drive gear assembly installed on the drive shaft; a driven gear assembly installed on the driven shaft; a belt having a gear formed on its inner surface 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 rotational radius of the drive gear assembly is inversely linked to the increase or decrease in the rotational radius of the driven gear assembly. The transmission controller comprises: first and second sleeves, each installed on the drive shaft, which slide and reciprocate in an axial direction parallel to the drive shaft and have screw threads formed on their outer circumference; and third and fourth sleeves, each installed on the driven shaft, which slide and reciprocate in an axial direction and have screw threads formed on their outer circumference. A hydraulic device comprising: an interlocking control member having an H shape and coupled at each of the four corners by the first to fourth sleeves and bearings; and a piston that reciprocates the interlocking control member in the axial direction; wherein the screw threads formed on the outer circumference of the first and second sleeves and the third and fourth sleeves are formed in mutually opposite directions, and further comprising a pressure position adjuster that controls the hydraulic device to move toward the side with a relatively larger radius of rotation between the driving gear assembly and the driven gear assembly to apply pressure to the interlocking control member, wherein the pressure position adjuster comprises: a guide gear installed in a direction parallel to the axial direction; a guide slot formed on the interlocking control member in a direction perpendicular to the axial direction; a control rod having one end fixedly coupled to the piston and reciprocating in the axial direction; and a rotary gear hinge-coupled to the other end of the control rod by a rotation restraint pin and meshing with the guide gear.It is configured to include a rotating arm, one end of which is hinge-coupled to the other end of a control rod by a rotational restraint pin and rotates by being restrained to the rotation of a rotating gear by a key of the rotational restraint pin, and the other end is restrained in the axial direction by a guide slot and maintained to be movable in a direction perpendicular to the axial direction.

Description

Technology Field

[0001] The present invention relates to a belt-type gear transmission that transmits rotational force of a drive shaft to a driven shaft, and more specifically, to a belt-type gear transmission in which a rotational radius varies by having a plurality of planetary gears arranged at equal intervals at a distance equal to the center of the shafts on the drive shaft and the driven shaft. Background Technology

[0002] A transmission is a device that converts and transmits the speed or rotational force of an engine or motor, and is generally classified into gear type and friction type.

[0003] A geared transmission is a multi-stage transmission that transmits power by changing it at fixed gear ratios, but it has the disadvantage of having a limited number of gears and complex shift control.

[0004] In contrast, friction transmissions can be implemented as belt or toroidal types; while both have the advantage of being continuously variable transmissions with continuously changing gear ratios, they have the disadvantage of significantly increased friction loss due to excessive pressure applied to the friction surfaces to prevent slippage, making it difficult to transmit large driving forces.

[0005] Accordingly, a belt-type gear transmission was introduced that can transmit large driving force while retaining the advantages of a continuously variable transmission by installing multiple planetary gears on the drive shaft and the dependent shaft, respectively, to vary the rotational radius of the planetary gears, and transmitting rotational force through the meshing of the planetary gears and the belt gears.

[0006] However, conventional belt-type gear transmissions have not yet reached proper commercialization because various problems remain unresolved, such as the difficulty in controlling the position of planetary gears during shifting, the difficulty for the planetary gears and belt gears to mesh precisely at the gear teeth and grooves as the rotational radius of the planetary gears changes continuously during shifting, the problem of the belt length connecting the planetary gears on the drive shaft and the planetary gears on the driven shaft varying as the rotational radius changes, and the problem of eccentricity occurring due to the difference in rotational radii between the drive shaft and the driven shaft. Prior art literature

[0007] Published Patent Application No. 10-2012-0010629 (February 6, 2012) Published Patent Application No. 10-2008-0083934 (September 19, 2008) WO 2012 / 011739 A2 (January 26, 2012) The problem to be solved

[0008] The present invention aims to provide a belt-type gear transmission that controls the drive side and the driven side in conjunction, which controls the rotational radius of the drive gear assembly of the drive shaft and the driven gear assembly of the driven shaft by means of linear reciprocating motion in a direction parallel to the drive shaft by a piston of a hydraulic device, thereby shifting gears, and also eliminates the change in belt length due to the change in rotational radius and the eccentricity phenomenon caused by the difference in rotational radius between the drive shaft and the driven shaft. means of solving the problem

[0009] To achieve the above objective, a belt-type gear transmission according to the present invention for transmitting rotational force of a drive shaft to a driven shaft comprises: a drive gear assembly installed on the drive shaft; a driven gear assembly installed on the driven shaft; a belt having a gear formed on its inner surface and connecting the drive gear assembly and the driven gear assembly to transmit rotational force of the drive shaft to the driven shaft; and a transmission controller for controlling transmission such that the increase or decrease in the rotational radius of the drive gear assembly is coupled in opposite directions to the increase or decrease in the rotational radius of the driven gear assembly.

[0010] In the above-described belt-type gear transmission, the transmission controller comprises: first and second sleeves, each installed on the drive shaft and sliding reciprocating in an axial direction parallel to the drive shaft, with screw threads formed on their outer circumference; third and fourth sleeves, each installed on the driven shaft and sliding reciprocating in the axial direction, with screw threads formed on their outer circumference; an interlocking control member having an H shape and coupled to the first to fourth sleeves by bearings at each of the four corners; and a hydraulic device having a piston that reciprocates the interlocking control member in the axial direction.

[0011] In the above-described belt-type gear transmission, the screw threads formed on the outer circumferences of the first and second sleeves and the third and fourth sleeves are formed in mutually opposite directions.

[0012] The above-described belt-type gear transmission further comprises a pressure position adjuster that controls the hydraulic device to move toward the side with the relatively larger radius of rotation between the drive gear assembly and the driven gear assembly to apply pressure to the interlocking control unit.

[0013] In the above-described belt-type gear transmission, the pressure position adjuster comprises: a guide gear installed in a direction perpendicular to the axial direction; a control rod having a gear on its outer circumference that meshes with the guide gear and is screw-coupled to the piston, rotating in response to the linear reciprocating motion of the piston and moving on the guide gear; and a roller groove fixedly coupled to the piston, which restrains the interlocking control rod in the axial direction and maintains it so that it can move in a direction perpendicular to the axial direction.

[0014] In the above-described belt-type gear transmission, the pressure position adjuster comprises: a guide gear installed in a direction parallel to the axial direction; a guide slot formed on the interlocking control table in a direction perpendicular to the axial direction; a control rod, one end of which is fixedly coupled to the piston and reciprocates in the axial direction; a rotating gear, which is hinge-coupled to the other end of the control rod by a rotation restraint pin and meshes with the guide gear; and a rotating arm, one end of which is hinge-coupled to the other end of the control rod by the rotation restraint pin and rotates while being constrained to rotate the rotating gear by a key of the rotation restraint pin, and the other end of which is constrained in the axial direction by the guide slot and maintained to be movable in a direction perpendicular to the axial direction.

[0015] The above-described belt-type gear transmission comprises: first and second interlocking control arm, each having one end fixedly coupled to the interlocking 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 first and second roller arms, each pin-coupled to the first and second supports and rotating by the inclined gear while pressing the belt by a roller; and further comprises 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 inclination gears of the first and second interlocking control arm, thereby causing the linear reciprocating motion of the interlocking control arm.

[0016] The above-described belt-type gear transmission further comprises: first and second interlocking control arm, each having one end fixedly coupled to the interlocking 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 one end equipped with an inclined gear that meshes with the inclined gear of the first and second interlocking control arm; and first and second roller arms, each hinged to the first and second supports and rotating by an inclined gear installed by extending from the first and second roller hinge extension rods coupled to one end, while pressing the belt by a roller provided at the other end.

[0017] In the above-described belt-type gear transmission, the first and second roller arms are each characterized by rotating toward the side with the smaller radius of rotation between the driving gear assembly and the driven gear assembly to apply pressure to the belt. Effects of the invention

[0018] According to the present invention, 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 by linear reciprocating motion in a direction parallel to the drive shaft by the piston of the hydraulic device, the rotation radius of the planetary gear can be adjusted to easily change gears.

[0019] 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 resolved by a roller device installed above and below the belt and operating in conjunction with linear reciprocating motion by a hydraulic device.

[0020] In addition, according to the present invention, the eccentricity caused by the difference in the rotational radius of the planetary gear between the driving shaft and the driven shaft can be resolved by adjusting the position where the interlocking control unit is pressurized by a pressurizing position adjuster that operates in conjunction with the linear reciprocating motion by a hydraulic device. Brief explanation of the drawing

[0021] FIG. 1a is a layout diagram illustrating the overall configuration of a belt-type gear transmission (first embodiment) according to the present invention. FIG. 1b is a layout diagram illustrating the overall configuration of a belt-type gear transmission (second embodiment) according to the present invention. FIG. 2a is a conceptual diagram for explaining the operation of a belt-type gear transmission (first embodiment) according to the present invention. FIG. 2b is a conceptual diagram for explaining the operation of a belt-type gear transmission (second embodiment) according to the present invention. FIG. 3 illustrates a first fixed plate installed on the driving shaft and the driven shaft, respectively. FIG. 3a illustrates a second fixed plate installed on the drive shaft and the driven shaft, respectively. FIG. 4 illustrates first and second rotating plates installed on a drive shaft. FIG. 4a illustrates first and second rotating plates installed on a driven shaft. Figure 5 illustrates the change in the rotating arm according to the change in the radius of rotation when the rotating arm is coupled to and arranged on a rotating plate. Figure 6 illustrates the various support plates. FIG. 7 illustrates (a) a cross-sectional view, (b) a plan view, (c) a support plate combined with a tension bolt, (d) a cover plate, (e) a gear piece, (f) a tension bolt, and (e) a twisted steel wire for a part of the belt. FIG. 8a illustrates a comparison of the driving states of a belt-type gear transmission (first embodiment) according to the present invention ((a) when the rotational speed is reduced, (b) when the rotational speed is increased). FIG. 8b illustrates a comparison of the driving states of a belt-type gear transmission (second embodiment) according to the present invention ((a) when the rotational speed is reduced, (b) when the rotational speed is increased). FIG. 9a illustrates a planar arrangement of a transmission controller (first embodiment) reinforced with a pressurized position adjuster. FIG. 9b illustrates a cross-sectional arrangement of the transmission controller (first embodiment) of FIG. 9a. FIG. 9c illustrates a planar arrangement of a transmission controller (second embodiment) reinforced with a pressurized position adjuster. FIG. 9d illustrates a cross-sectional arrangement of the transmission controller (second embodiment) of FIG. 9c. FIG. 10a is a drawing for explaining the configuration and operation of a roller device (first embodiment). FIG. 10b illustrates the arrangement of a transmission controller (first embodiment) reinforced with a roller device. FIG. 10c is a drawing for explaining the configuration and operation of a roller device (second embodiment). FIG. 10d illustrates the arrangement of a transmission controller (second embodiment) reinforced with a roller device. FIG. 11a is a cross-sectional view illustrating the overall configuration of a planetary gear (first embodiment). FIG. 11b is a cross-sectional view illustrating the overall configuration of a planetary gear (second embodiment). FIG. 12a illustrates (a) an inner sleeve, (b) a left pin, and (c) a right pin constituting the main body in FIG. 11a. FIG. 12b illustrates (a) the outer sleeve, (b) the left fixing screw, and (c) the right fixing screw constituting the gear sleeve in FIG. 11a. FIG. 12c illustrates (a) the main spring, (b) the left support plate, and (c) the right support plate constituting the bidirectional buffer in FIG. 11a. FIG. 12d illustrates (a) a compression rod and (b) a pressure regulating pin constituting the spring pressure regulator in FIG. 11a. FIG. 12e illustrates (a) a left rotational pressure ring, (b) a left support ring, (c) an auxiliary spring, (d) a right support ring, and (e) a right rotational pressure ring constituting the rotational induction device in FIG. 11a. Fig. 12f illustrates the rotary assist ring in Fig. 11a. FIG. 12g illustrates (a) the left pin and (b) the right pin constituting the main body in FIG. 11b. FIG. 12h illustrates (a) the outer sleeve, (b) the left fixing screw, and (c) the right fixing screw constituting the gear sleeve in FIG. 11b. FIG. 12i illustrates (a) the main spring, (b) the left support plate, and (c) the right support plate constituting the bidirectional buffer in FIG. 11b. FIG. 12j illustrates (a) a compression rod and (b) a pressure regulating pin constituting the spring pressure regulator in FIG. 11b. FIG. 12k illustrates (a) a left rotational pressure ring, (b) a left support ring, (c) an auxiliary spring, (d) a right support ring, and (e) a right rotational pressure ring constituting the rotational induction device in FIG. 11b. Fig. 12l illustrates the rotary assist ring in Fig. 11b. FIG. 13 is a diagram illustrating the rotation and movement of a gear sleeve when a gear provided on a belt meshes with a gear provided on a planetary gear in the direction of rotational travel. FIG. 13a is a diagram illustrating the rotation and movement of a gear sleeve when a gear provided on a belt meshes with a gear provided on a planetary gear at the rear of the rotational direction of the gear. Figure 14 shows the main spring pressure when (a) the drive shaft torque is small and (b) the drive shaft torque is large. Specific details for implementing the invention

[0022] Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the attached drawings.

[0023] FIG. 1a is a layout diagram illustrating 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 a belt-type gear transmission according to the present invention. FIG. 1b is a layout diagram illustrating 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 a belt-type gear transmission according to the present invention.

[0024] 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 transmission controller (40). 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 transmission controller (40b).

[0025] 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 circumference of the driving shaft (1) and the driven shaft (2), respectively.

[0026] First, referring to FIGS. 1a and FIGS. 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 a angular support plate (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 a angular support plate (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 radius of rotation.

[0027] The planetary gears (11) constituting the drive gear assembly (10) have gears formed on a part of their outer circumference that mesh with the gears of the belt (30), and it is preferable that six of them be arranged at equal intervals at a distance equal to 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.

[0028] In the drive gear assembly (10), a first fixed plate (12a) and a first rotating plate (13a) are installed on the right side with the planetary gear (11) in between, and a angular support plate (15), a second fixed plate (12b), and a second rotating plate (13b) are installed in sequence on the left side. For convenience of explanation, the direction in which the fixed plate (12), the rotating plate (13), and the angular support plate (15) each face the planetary gear (11) is defined as the inner side, and the opposite direction is defined as the outer side.

[0029] FIG. 3 illustrates a first fixed plate (12a, 22a) installed on a drive shaft (1) and a driven shaft (2), respectively, and FIG. 3a illustrates a second fixed plate (12b, 22b) installed on a drive shaft (1) and a driven shaft (2), respectively, and the shape of the plates is all viewed from the left side as shown in FIG. 1.

[0030] The fixed plate (12) that is constrained to the drive shaft (1) is a disc-shaped plate with a through hole in the center, and is equipped with a coupling key (12_1) on its inner circumference so as to be fixedly coupled to an axial groove (1_1) formed on the outer circumference of the drive shaft (1) and rotates integrally with the drive shaft (1). On the fixed plate (12), six planetary gear guide slots (12a_2) are formed at equal intervals, forming a curved shape that bends clockwise toward the center of the disc when viewed from the left side (the number can be selected from 5 to 8, just like the number of planetary gears (11)). The right end (right pin (113)) of the corresponding planetary gear (11) is restrained in 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 restrained in the planetary gear guide slot (12b_2) of the second fixed plate (12b).

[0031] In addition, 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.

[0032] FIG. 4 illustrates first and second rotating plates (13) installed on a drive shaft (1), (a) is a plan view of the rotating plate (13) viewed from the inside to the outside, (b) is a cross-sectional view of the second rotating plate (13b) coupled with the rotating 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 drive shaft (1), (e) is a conceptual view of the first sleeve (41a), and (f) is a cross-sectional view of the first rotating plate (13a) coupled with the rotating arm (14).

[0033] In the drive gear assembly (10), the first and second rotating plates (13a, 13b) are each installed on the outer side of the corresponding first and second fixed plates (12a, 12b) in the shape of a disc. A cylinder with a screw (13_1) formed on its inner circumference is integrally formed in the center of the rotating plate (13), and is screw-coupled to the outer circumference of a sleeve (41) coupled to the groove (1_1) of the drive shaft (1) by a coupling key (41_1), thereby being constrained to the rotation of the drive shaft (1) just like the fixed plate (12).

[0034] Additionally, the sleeve (41) is coupled to the groove (1_1) of the drive shaft (1) by the coupling key (41_1), so that the rotation of the drive shaft (1) is constrained but slides back and forth in the axial direction. The rotating plate (13), which is screw-coupled to the sleeve (41), rotates within a certain range in a 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).

[0035] FIG. 5 illustrates the change of the rotating arm according to the change in the radius of rotation while the rotating arm (14) is coupled to and arranged on the rotating plate (13).

[0036] Referring to FIG. 5, six rotating arms (14) are arranged on each of the first and second rotating plates (13a, 13b), and one end of each rotating arm (14) is hinged at equal intervals to the periphery of the first and second rotating plates (13a, 13b). The other end of each rotating arm (14) is hinged to the end (left pin (112) or right pin (113)) of a planetary gear (11) whose movement is restricted by the corresponding planetary gear guide slot (12_2) of the corresponding fixed plate (12). That is, the other end of the rotating arm (14), which has one end hinged to the first rotating plate (13a), is hinged to the right end (right pin (113)) of the corresponding planetary gear (11), and the other end of the rotating arm (14), which has one end hinged to the second rotating plate (13b), is hinged to the left end (left pin (112)) of the corresponding planetary gear (11).

[0037] Referring to FIG. 5, it is preferable that the end portion and the other portion of the rotating arm (14) be formed by being bent toward the center of the rotating plate (13), and according to FIG. 4 and FIG. 4a, it is preferable that the end portion (14_1) of the rotating arm (14) operates on the outer plane of the rotating plate (13) and the other portion (14_2) operates on the inner plane of the rotating plate (13). Accordingly, as shown in FIG. 4 and FIG. 4a, the end portion (14_1) and the other portion (14_2) of the rotating arm (14) are formed by being bent in two portions so that the rotating arm (14) can rotate on two planes, and it is preferable that a rotating arm through groove (13_2) is formed in the periphery of the rotating plate (13) so that the rotating arm (14) can pass through.

[0038] Referring to FIG. 6, the planetary support plate (15) is a disc-shaped plate installed on the inner side of the second fixed plate (12b), and a number of normal slots (15_1) in the normal direction are formed at equal intervals. The planetary support plate (15) is not fixedly coupled to the drive shaft (1). The normal slots (15_1) of the planetary support plate (15) restrain the coupling projection (112_1) provided on the outer circumference of the left pin (112) of the planetary gear (11), so that even if the planetary gear (11) moves closer to or further away from the drive shaft (1), the direction of the planetary gear (11) is maintained constant with respect to the normal direction.

[0039] In the driven gear assembly (20), similar to the driving gear assembly (10), the first fixed plate (22a) and the first rotating plate (23a) are installed on the right side with the planetary gear (21) in between, and the angle support plate (25), the second fixed plate (22b), and the second rotating plate (23b) are installed in sequence 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 angle support plate (25) constituting the driven gear assembly (20) are substantially identical to 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 angle support plate (15) constituting the driving gear assembly (10), respectively.

[0040] However, since the rotational direction of the rotating plate (23) relative to the fixed plate (22) in the driven gear assembly (20) is opposite to the rotational direction of the rotating plate (13) relative to the fixed plate (12) in the driving gear assembly (10), the screw (23_1) for the rotating plate (23) in FIG. 4b to be coupled with the sleeve (41) is formed in the opposite direction to the screw (13_1) for the rotating plate (13) in FIG. 4 to be coupled with the sleeve (41). Additionally, the spring pressure adjustment guide gear (22a_3) formed in the planetary gear guide slot (22a_2) of the first fixed plate (22a) 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 driving gear assembly (10).

[0041] The driving 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 driving 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 driving gear assembly (20) constituting the first embodiment of the belt-type gear transmission according to the present invention, except that all other components are identical.

[0042] Referring to FIG. 7, the belt (30) in the present invention is composed of a plurality of gear pieces (31) that are joined to a plurality of strands of twisted steel wire (32) by tension bolts (33).

[0043] A support plate (34) is installed between the gear piece (31) and the twisted steel wire (32). The support plate (34) is provided with steel wire receiving grooves (34_1) formed with a grain similar to the twist of the twisted steel wire (32), corresponding to the number of strands of the twisted steel wire (32) to prevent slipping, and is provided with slot-shaped bolt holes (34_2).

[0044] A support plate (34) is installed on a gear piece (31), and a twisted steel wire (32) is installed in the steel wire receiving groove (34_1) of the support plate, and a cover plate (35) is installed, and by repeatedly tightening all of these with a tension bolt (33), a number of gear pieces (31) are combined with a number of strands of twisted steel wire (32) to manufacture a belt (30).

[0045] In a preferred embodiment of the present invention, the gear provided on the belt (30) is not formed parallel to the axial direction but is formed at an angle (20° to 40°, preferably 35°) from the axial direction. The function of the inclined gear formed on the belt (30) will be explained in detail in the description of the planetary gear (11).

[0046] Referring again to FIG. 1a and FIG. 1b, the transmission controller (40, 40b) in the present invention comprises first to fourth sleeves (41a, 41b, 41c, 41d), interlocking control bands (43, 43b), and a hydraulic device (44).

[0047] The first sleeve (41a) and the second sleeve (41b) are installed on the drive shaft (1) and rotate together with the drive shaft (1) while sliding back and forth in the axial direction, and the third sleeve (41c) and the fourth sleeve (41d) are installed on the driven shaft (2) and rotate together with the driven shaft (2) while sliding back and forth in the axial direction. As shown in FIGS. 4 and 4a, the first to fourth sleeves (41a, 41b, 41c, 41d) all have screws formed on their outer circumference, 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) have opposite directions.

[0048] The interlocking control unit (43, 43b) forms an overall H shape and is connected at each of the four corners by the first to fourth sleeves (41a, 41b, 41c, 41d) and the bearing (42), so that the first to fourth sleeves (41a, 41b, 41c, 41d) interlock and reciprocate on the corresponding shaft (drive shaft (1) or driven shaft (2)).

[0049] The hydraulic device (44) is equipped with a piston (45) to control the interlocking control unit (43, 43b) to reciprocate in the axial direction.

[0050] The operation process of the transmission controller (40, 40b) is as follows.

[0051] The hydraulic device (44) moves the interlocking control unit (43, 43b) in the axial direction (i.e., in a direction parallel to the drive shaft (1) and the driven shaft (2)) by means of the piston (45). When the interlocking control unit (43, 43b) moves in the axial direction, the first to fourth sleeves (41a, 41b, 41c, 41d), which are constrained by bearings (42) at the four corners of the interlocking control unit (43, 43b), move along the grooves (1_1, 2_1) installed on the corresponding shafts. At this time, the rotating plate (13, 23) screw-coupled to the sleeve (41) cannot move together with the sleeve (41) at the installed position and rotates relative to the fixed plate (12, 22). Since both ends of the planetary gears (11, 21, 11b, 21b) are hinged to the rotating plate (13, 23) by the rotating arm (14, 24), the rotation of the rotating plate (13, 23) causes the planetary gears (11, 21, 11b, 21b), whose movement path is constrained by the planetary gear guide slot (12_2, 22_2) of the fixed plate (12, 22), to move to the center or periphery of the shaft (driving shaft (1) or driven shaft (2)), thereby changing the rotation radius of the driving gear assembly (10, 10b) and the driven gear assembly (20, 20b).

[0052] FIG. 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 rotational speed is reduced and (b) is when the rotational speed is increased.

[0053] First, when reducing the rotational speed as illustrated in (a) of FIG. 8a, when the rotating plate (13a, 13b) of the drive shaft (1) rotates clockwise with respect to the fixed plate (12a, 12b), the planetary gear (11) hinged to the rotating arm (14) hinged to the rotating 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) decreases, thereby reducing the radius of rotation.

[0054] In addition, the rotating plates (23a, 23b) provided on the driven shaft (2) rotate counterclockwise relative to the fixed plates (22a, 22b), thereby increasing the distance between the position of the planetary gear (21), which is hinge-constrained to the rotating arm (24) hinge-constrained to the rotating plates (23a, 23b), and the driven shaft (2), so that the radius of rotation increases. In this state, the belt (30) connects the planetary gears (11, 21) of both shafts (drive shaft (1) and driven shaft (2)) to transmit rotational force, so the rotational speed decreases.

[0055] Meanwhile, when the rotational speed is increased, if the rotating plate (13a, 13b) of the drive shaft (1) rotates counterclockwise with respect to the fixed plate (12a, 12b), the planetary gear (11) hinged to the rotating arm (14) hinged to the rotating 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, thereby increasing the radius of rotation.

[0056] In addition, the rotating plates (23a, 23b) provided on the driven shaft (2) rotate clockwise relative to the fixed plates (22a, 22b), thereby reducing the radius of rotation by bringing the position of the planetary gear (21), which is hinge-constrained to the rotating arm (24) hinge-constrained to the rotating plates (23a, 23b), closer to the driven shaft (2). In this state, the belt (30) connects the planetary gears (11, 21) of both shafts (drive shaft (1) and driven shaft (2)) to transmit rotational force, thereby increasing the rotational speed.

[0057] FIG. 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 rotational speed is reduced and (b) is when the rotational speed is increased.

[0058] The operation of Fig. 8b is the same as the operation of Fig. 8a.

[0059] 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 interlocking control unit (43) to reduce side effects caused by eccentricity resulting from the difference in rotational radius between the driving gear assembly (10) and the driven gear assembly (20).

[0060] The pressure position adjuster (46) is equipped with a guide gear (46_1), a control rod (46_2), and a roller groove (46_3).

[0061] The guide gear (46_1) is installed in a straight line in a direction perpendicular to the drive shaft (1).

[0062] The control rod (46_2) is screw-coupled with the piston (45) and rotates in response to the linear reciprocating motion of the piston (45), and the gear provided on the outer circumference meshes with the guide gear (46_1) and moves on the guide gear (46_1) in a direction perpendicular to the drive shaft (1).

[0063] The roller groove (46_3) is fixedly coupled to the piston (45) and restrains the interlocking control unit (43) in the axial direction while allowing it to move in a direction perpendicular to the axis.

[0064] Accordingly, when the piston (45) of the hydraulic device (44) moves in the axial direction, the control rod (46_2) screw-coupled to the piston (45) moves on the guide gear (46_1) because the gear provided on the outer circumference meshes with the guide gear (46_1) and rotates. 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 interlocking control rod (43) in the axial direction so that the piston (45) moves freely in the direction perpendicular to the axis, while restraining the interlocking control rod (43) so that the interlocking control rod (43) can reciprocate in the axial direction.

[0065] Referring to FIG. 9c to 9b_1, the transmission controller (40b) according to the second embodiment of the present invention includes a pressure position adjuster (46b) with a different configuration from the pressure position adjuster (46) included in the transmission controller (40) according to the first embodiment of the present invention.

[0066] The pressure position adjuster (46b) is equipped with a guide gear (46b_1), a control rod (46b_2), a rotating gear (46b_3), a rotating arm (46b_4), a rotation restraint pin (46b_7), and an interlocking control unit restraint pin (46b_5), and the interlocking control unit (43b) is equipped with a guide slot (43b_3) formed in a direction perpendicular to the drive shaft.

[0067] The guide gear (46b_1) is installed in a straight line in a direction parallel to the drive shaft (1).

[0068] 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 hinged to the rotating gear (46b_3) and rotating arm (46b_4) by the rotation restraint pin (46b_7), and reciprocates axially along the piston (45).

[0069] 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 on 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.

[0070] 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) moves back and forth.

[0071] One end of the rotating arm (46b_4) is constrained to the rotating gear (46b_3) by the rotational restraint pin (46b_7), but the other end is constrained to the guide slot (43b_3) of the interlocking control unit (43b) by the interlocking control unit restraint pin (46b_5), thereby allowing it to move freely in the vertical direction of the axial direction and controlling the interlocking control unit (43b) to move back and forth in the axial direction.

[0072] Ultimately, the pressure position adjuster (46, 46b) according to the present invention can reduce adverse effects caused by eccentricity resulting from the difference in rotation radius by controlling the hydraulic device (44) to move toward the side with the relatively larger rotation radius between the driving gear assembly (10, 10b) and the driven gear assembly (20, 20b) to apply pressure to the interlocking control unit (43, 43b).

[0073] Referring to FIG. 10a and FIG. 10b, the transmission controller (40) according to the first embodiment of the present invention further includes a roller device (48) that corrects the difference in belt length caused by the difference in rotational radius between the driving gear assembly (10) and the driven gear assembly (20).

[0074] The roller device (48) is equipped with first and second supports (48_1), first and second roller arms (48_2), a roller (48_3), and first and second interlocking control arms (43_1).

[0075] The first and second supports (48_1) are installed at a constant distance above and below the belt (30) connected between the drive gear assembly (10) and the driven gear assembly (20).

[0076] The first and second roller arms (48_2) are hinged to the first and second supports (48_1), respectively, and rotate by means of an inclined gear (48_4) provided at one end, while pressing the belt (30) by means of a roller (48_3) provided at the other end.

[0077] The first and second interlocking control arms (43_1) each have one end fixedly connected to the interlocking control arm (43), and the other end is equipped with an inclined gear (43_2).

[0078] When the interlocking control unit (43) moves in a straight line by the piston (45) of the hydraulic device (44), the first and second interlocking control unit arms (43_1) fixedly coupled to the interlocking control unit (43) also move in a straight line along with the interlocking control unit (43). Accordingly, the first and second roller arms (48_2) rotate within a certain range by the inclined gear (43_2) provided on the first and second interlocking control unit arms (43_1) and the inclined gear (48_4) provided on the first and second roller arms (48_2). At this time, the first and second roller arms (48_2) each rotate toward the side with the smaller radius of rotation between the driving gear assembly (10) and the driven gear assembly (20) to apply pressure to the belt (30). By appropriately adjusting the radius of rotation and the range of rotation of the first and second roller arms (48_2), the difference in belt length caused by the difference in the radius of rotation between the driving gear assembly (10) and the driven gear assembly (20) is reduced to within an allowable range.

[0079] Referring to FIG. 10c and FIG. 10d, the transmission controller (40b) according to the second embodiment of the present invention further includes a roller device (48b) that corrects the difference in belt length caused by the difference in rotational radius between the driving gear assembly (10b) and the driven gear assembly (20b).

[0080] The roller device (48b) is equipped with first and second supports (48b_1), first and second roller arms (48b_2), a roller (48b_3), first and second interlocking control arms (43b_1), and first and second roller hinge extension rods (48b_5).

[0081] The first and second supports (48b_1) are installed at a constant distance above and below the belt (30) connected between the drive gear assembly (10b) and the driven gear assembly (20b).

[0082] The first and second interlocking control arms (43b_1) each have one end fixedly connected to the interlocking control arm (43b), and the other end is equipped with an inclined gear (43b_2).

[0083] The first and second roller hinge extension rods (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 interlocking control arms (43b_1), and the other end is fixedly coupled to one end of the first and second roller arms (48b_2).

[0084] The first and second roller arms (48b_2) are hinged to the first and second supports (48b_1), respectively, and rotate by means of the first and second roller hinge extension rods (48b_5) connected to one end, while pressing the belt (30) by means of the roller (48b_3) provided at the other end.

[0085] When the interlocking control unit (43b) moves in a straight line, the first and second interlocking control unit arms (43b_1) fixedly coupled to the interlocking control unit (43b) also move in a straight line, and accordingly, the first and second roller hinge extension rods (48b_5) that are gear-coupled by the inclined gear (43b_2) provided on the first and second interlocking control unit arms (43b_1) and the inclined gear (48b_4) provided on the unit itself rotate.

[0086] As the first and second roller hinge extension rods (48b_5) rotate, the first and second roller arms (48b_2), which are keyed to the first and second roller hinge extension rods (48b_5), rotate within a certain range.

[0087] At this time, the first and second roller arms (48b_2) each rotate toward the side with the smaller radius of rotation between the driving gear assembly (10b) and the driven gear assembly (20b) to apply pressure to the belt (30). By appropriately adjusting the radius of rotation and the range of rotation of the first and second roller arms (48b_2), the difference in the length of the belt (30) caused by the difference in the radius of rotation between the driving gear assembly (10b) and the driven gear assembly (20b) is reduced to within an allowable range.

[0088] Referring to FIG. 11a, a planetary gear (11, 21) according to the first embodiment of the present invention comprises a main body (110), a gear sleeve (120), a bidirectional dampener (130), a spring pressure regulator (140), and a rotation inducer (150).

[0089] The main body (110) of the planetary gear (11) includes an inner sleeve (111) ((a) in FIG. 12a), a left pin (112) ((b) in FIG. 12a) located to the left of the inner sleeve (111), and a right pin (113) ((c) in FIG. 12a) located to the right of the inner sleeve (111).

[0090] The inner sleeve (111) is cylindrical in shape and accommodates a bidirectional buffer (130) inside.

[0091] The left pin (112) is hinged to the rotating arm (14) which is hinged to the second rotating plate (13b), and moves by being constrained to the planetary gear guide slot (12_2) of the second fixed plate (12b) according to the rotation of the second rotating plate (13b). At this time, the coupling projection (112_1) provided on the left pin (112) is constrained by the normal slot (15_1) of the rotating plate (15), so that other components connected to the left pin (112) can also maintain a constant angle with the normal determined by the normal slot (15_1).

[0092] In contrast, one end of the right pin (113) is hinged to a rotating arm (14) that is hinged to the first rotating plate (13a). A spring pressure adjusting gear (113_1) is formed on the outer circumference of the other end of the right pin (113), so that when the first rotating plate (13a) rotates, it engages with a spring pressure adjusting guide gear (12_3) formed in the planetary gear guide slot (12_2) of the first fixed plate (12a), rotates, and moves while being constrained by the planetary gear guide slot (12_2).

[0093] 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).

[0094] The outer sleeve (121) is in the form of a cylinder that wraps around a part of the main body (110), is coupled to be movable left and right around the main body (110) and rotatable within a fine range, and a gear (121_1) is formed on at least a part of the outer circumference that meshes with the gear of the belt (30) and maintains an inclination at a constant angle (θ) with respect to the axial direction. Here, θ is 20° to 40°, and it is preferable to maintain it at approximately 35°.

[0095] In the gear provided on the belt (30) and the gear (121_1) provided on the gear sleeve (120), the gear teeth form a curved surface, and the radius of the curved surface of the gear teeth is made at least twice as large as the radius of the gear sleeve (120) to smooth out the fine rotation of the gear sleeve (120) during gear shifting.

[0096] 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 components inside. The left fixing screw (122) and the right fixing screw (123) function to transmit pressure resulting from the left and right movement of the gear sleeve (120) to other components (left support plate (132), rotation assist ring (161) (Fig. 12f)).

[0097] The bidirectional damper (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 dampens the left and right movement of the gear sleeve (120) to limit it within a certain range.

[0098] The left support plate (132) is supported on the left by the left pin (112) so that it cannot move further, but on the right by the left fixing screw (122) so that it can move within a certain range (approximately 1 / 2 pitch) while pressing the main spring (131) inside the inner sleeve (111).

[0099] The right support plate (133) is supported to the right by the compression rod (141) described below and cannot move further, but to the left it is pressed by the compression rod (141) and can move up to a certain range (approximately 1 / 2 pitch) while pressing the main spring (131) within the inner sleeve (111).

[0100] 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 radius of rotation is large relative to the drive shaft (1), and increases the pressure of the main spring (131) when the radius of rotation is small.

[0101] The compression rod (141) is in the shape of a cylinder with a screw formed on its inner circumference and is screw-coupled 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).

[0102] One end of the pressure regulating pin (142) is integrally connected with the right pin (113) and rotates together with the right pin (113). Additionally, the other end of the pressure regulating pin (142) has a screw formed on its outer circumference and is screw-coupled with the inner circumference of the compression rod (141). Between the one end and the other end of the pressure regulating pin (142), a regulating projection (142_1) is formed on its outer circumference. The leftward movement pressure of the gear sleeve (120) is transmitted from the right fixing screw (123) to the regulating projection (142_1) through the rotation assist ring (161) (Fig. 12f), thereby moving the pressure regulating pin (142) to the left.

[0103] The rotation guide (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 within a fine range in response to the left-right movement pressure of the gear sleeve (120), and provides auxiliary cushioning for the left-right movement of the gear sleeve (120).

[0104] The left rotation pressure ring (152) is coupled to the gear sleeve (120) and rotates synchronously, and has one end receiving rightward movement pressure from the gear sleeve (120) and the other end having a side inclined groove (152_1) formed therein.

[0105] The left support ring (153) is positioned to the left of the auxiliary spring (151) and is installed so as to be movable only to the right from the compression rod (141). A side inclination key (153_1) corresponding to the side inclination groove (152_1) of the left rotational pressure ring (152) is formed at one end, and the other end supports the auxiliary spring (151).

[0106] The right rotational pressure ring (155) is coupled to the gear sleeve (120) and rotates synchronously, and has one end receiving leftward movement pressure from the gear sleeve (120) and the other end having a side inclined groove (155_1) formed therein.

[0107] The right support ring (155) is positioned to the right of the auxiliary spring (151) and is installed so as to be movable only to the left from the compression rod (141). A side inclination key (154_1) corresponding to the side inclination groove (155_1) of the right rotational pressure ring (155) is formed at one end, and the other end supports the auxiliary spring (151).

[0108] The left rotational pressure ring (152) and the right rotational pressure ring (154) of the rotational inducer (150) rotate in mutually opposite directions within a fine range in response to the moving pressure from the gear sleeve (120), thereby rotating the rotationally synchronized gear sleeve (120).

[0109] In the case of the planetary gear (11) according to the present invention, a rotational assist ring (161) (Fig. 12f) having an inner key (161_2) at one end in a ring shape and an outer key (161_1) formed to be offset about 2 / 3 of the clockwise side of the keyway slope compared to the inner key (161_2) is installed between the right rotational pressure ring (154) and the right fixing screw (123). The outer key (161_1) of the rotation assist ring (161) is coupled to a groove provided in the right rotation pressure ring (154), and the inner key (161_2) is coupled to a groove provided in the adjustment projection (142_1) of the pressure adjustment pin (142) by about 1 / 3. When the other end of the rotation assist ring (161) is pressed against the right fixing screw (123), the inner key (161_2) is coupled to the key on the pressure adjustment pin (142) and rotates partially, while the outer key (161_1) first presses the right rotation pressure ring (154), thereby supporting the rotation of the gear sleeve (120).

[0110] According to the present invention, when a gear (121_1) provided in a planetary gear (11) comes into contact with a gear (30_1) provided in a belt (30), during the gear shifting process, gear teeth do not mesh with gear teeth but rather gear teeth come into contact with gear teeth. Such a 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 in the planetary gear (11) and the gear (30_1) provided in 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, thereby causing the gear (121_1) provided in the planetary gear (11) to move 1 / 2 pitch in the axial direction from the gear provided in the belt (30) so that the gear teeth and gear teeth of both gears mesh.

[0111] Hereinafter, the operation process of the bidirectional damper (130) of the planetary gear (11) according to the present invention will be described in detail. The bidirectional damper (130) causes the gear sleeve (120) to move left and right relative to the main body (110) so that the gear (121_1) provided in the planetary gear (11) meshes with the gear (30_1) provided in the belt (30).

[0112] When the gear (30_1) provided on the belt (30) meshes with the gear (121_1) provided on the planetary gear (11) in the direction of rotation (see FIG. 13 (a)), the planetary gear (11) is pushed to the left in the direction of rotation of the belt (30) by the axial force generated, and the right fixing screw (123) coupled to the outer sleeve (121) presses the rotation assist ring (161) (see FIG. 13 (c)). Accordingly, the gear provided on the rotation assist ring (161) partially rotates and presses the gear provided on the adjustment projection (142_1) of the pressure adjustment pin (142) which is in a partially meshed state, and the pressure adjustment pin (142) presses the main spring (131) by means of the screw-coupled compression rod (141) and the right support plate (133). At this time, the main spring (131) is supported by a left support plate (131) which is supported by a left pin (112) of the planetary gear (11) supported by a second fixed plate (12b). Accordingly, the leftward movement of the gear sleeve (120) in the planetary gear (11) is limited to within a certain range (see (d) of FIG. 13).

[0113] 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 of the rotational direction of travel (see FIG. 13a (a)), the planetary gear (11) is pushed to the right in the rotational direction of travel of the belt (30), and the left fixing screw (122) coupled to the outer sleeve (121) presses the left support plate (132) (see FIG. 13a (c)), and the left support plate (132) presses the main spring (131). At this time, the compression rod (141), which is screw-coupled with the pressure regulating pin (142) supported by the first fixing plate (12a), supports the main spring (131) with the right support plate (133). Therefore, the movement of the gear sleeve (120) to the right in the planetary gear (11) is limited to within a certain range (see FIG. 13a (d)).

[0114] Hereinafter, the operation process of the rotation guide (150) of the planetary gear (11) according to the present invention will be described in detail. The rotation guide (15) is an auxiliary device that facilitates movement left and right relative to the main body (110) by rotating the gear sleeve (120) within a fine range relative to the main body (110) in a section adjacent to a specific point where the gear (121_1) of the planetary gear (11) and the gear (30_1) provided on the belt (30) mesh excessively with each other.

[0115] When the gear provided on the belt (30) meshes with the gear (121_1) provided on the planetary gear (11) in the direction of rotation (see FIG. 13 (a)), the right rotational pressure ring (155) rotates synchronously with the outer sleeve (121) by having a key provided on its outer circumference constrained in a groove provided on the inner circumference of the outer sleeve (121). The right fixing screw (123) supports the rotational assist ring (161), and the outer key (161_1) provided on the rotational assist ring (161) is coupled with the groove provided on the right rotational pressure ring (155). Additionally, one end of the right rotational pressure ring (155) is provided with a side inclined groove (155_1) and makes unidirectional sliding contact with a side inclined key (154_1) provided on one end of the right support ring (154). Accordingly, when the right rotational pressure ring (155) presses the right support ring (154) in a direction facing it, rotation occurs between them within a fine range. At this time, the key provided on the inner circumference of the right support ring (154) is constrained in the groove provided on the outer circumference of the compression rod (141) so that rotation is suppressed, and since the compression rod (141) is coupled in a state where it does not rotate relative to the inner sleeve (111), the outer sleeve (121), which rotates in sync with the right rotational pressure ring (155) by the pressure of the right fixing screw (123), undergoes fine rotation relative to the main body (110) (see FIG. 13 (b)). The right support ring (154), whose rotation is suppressed, moves to the left and presses the auxiliary spring (151).

[0116] Meanwhile, when the gear provided on the belt (30) meshes with the gear provided on the planetary gear (11) in the direction of rotation (see (a) in FIG. 13a), the left rotational pressure ring (152) rotates synchronously with the outer sleeve (121) by having a key provided on its outer circumference constrained in a groove provided on the inner circumference of the outer sleeve (121). One end of the left rotational pressure ring (152) is supported at the end of the groove provided on the outer sleeve (121). One end of the left rotational pressure ring (152) is provided with a side inclined groove (152_1) and makes unidirectional sliding contact with a side inclined key (153_1) provided on one end of the left support ring (153). Therefore, when the left rotational pressure ring (152) presses the left support ring (153) in a direction facing it, rotation occurs between them within a fine range.

[0117] At this time, the key provided on the inner circumference of the left support ring (153) is constrained in the groove provided on the outer circumference of the compression rod (141), thereby suppressing rotation. Since the compression rod (141) is coupled in a state where it does not rotate relative to the inner sleeve (111), the outer sleeve (121), which rotates in sync with the left rotational pressure ring (152) by the pressure of the left fixing screw (122), undergoes a fine rotation relative to the main body (110) (see Fig. 13a (b)). The left support ring (153), whose rotation is suppressed, moves to the right and presses the auxiliary spring (151).

[0118] When combining the operation process of the bidirectional buffer (130) and the rotation inducer (150), when the gear (30_1) provided on the belt (30) meshes with the gear (121_1) provided on the planetary gear (11) in the front of the rotational direction, as shown in FIG. 13 (b), the gear sleeve (120) of the planetary gear (11) moves to the rear of the rotational direction of the gear (121_1) by rotating slightly to the boundary between the curved portion formed on the gear crest and the gear inclined surface, and then moves to the gear inclined surface, as shown in FIG. 13 (d), the gear sleeve (120) of the planetary gear (11) moves further to the left to the gear groove, thereby causing both gears to mesh in a complete state.

[0119] Meanwhile, when the gear (30_1) provided on the belt (30) meshes with the gear (121_1) provided on the planetary gear (11) in the rear direction of rotation, as shown in (b) of FIG. 13a, the gear sleeve (120) of the planetary gear (11) moves to the front direction of rotation of the gear (121_1) by rotating slightly to the boundary between the curved portion formed on the gear crest and the gear inclined surface, and then moves to the gear inclined surface, 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, thereby ensuring that both gears mesh in a complete state.

[0120] The operation process of the spring pressure regulator (140) of the planetary gear (11) according to the present invention will be explained in detail below.

[0121] The main spring (131) provided in the bidirectional damper (130) needs to reduce the spring pressure when the torque is low (i.e., when the radius of rotation is large) relative to the drive shaft (1) (see Fig. 14 (a)) and increase the spring pressure when the torque is high (i.e., when the radius of rotation is small) (see Fig. 14 (b)). 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 radius of rotation of the drive shaft.

[0122] A guide gear (12_3) for adjusting spring pressure is formed in the planetary gear guide slot (12_2) of the first fixed plate (12a) of the drive gear assembly (10), and meshes with the spring pressure adjusting gear (113_1) formed on the outer circumference of the right pin (113) of the planetary gear (11). Accordingly, 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 adjusting pin (142) is coupled to a groove formed on the inner circumference of the right pin (113), so that the pressure adjusting pin (142) rotates together with the right pin (113). A screw is formed on the outer circumference of the other end of the pressure adjusting pin (142) and is screw-coupled with the inner circumference of the compression rod (141). Accordingly, the rotationally restricted compression rod (141) reciprocates in a straight line by the rotation of the pressure regulating pin (142) and supports the right support plate (133) 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 a direction opposite to that of 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) in the driving gear assembly (10) and the planetary gear (21) in the driven gear assembly (20) can maintain the same pressure of the main spring (131).

[0123] Referring to FIG. 11b, a planetary gear (11b, 21b) according to a second embodiment of the present invention comprises a main body (110b), a gear sleeve (120b), a bidirectional dampener (130b), a spring pressure regulator (140b), and a rotation inducer (150b).

[0124] 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.

[0125] The left pin (112b) is hinged to the rotating arm (14) which is hinged to the second rotating plate (13b), and moves by being constrained to the planetary gear guide slot (12_2) of the second fixed plate (12b) according to the rotation of the second rotating plate (13b). At this time, the coupling projection (112b_1) provided on the left pin (112b) is constrained by the normal slot (15_1) of the rotating plate (15), so that other components connected to the left pin (112b) can also maintain a constant angle with the normal determined by the normal slot (15_1).

[0126] In contrast, one end of the right pin (113b) is hinged to a rotating arm (14) that is hinged to the first rotating plate (13a). A spring pressure adjusting gear (113_1) is formed on the outer circumference of the other end of the right pin (113b), so that when the first rotating plate (13a) rotates, it engages with a spring pressure adjusting guide gear (12_3) formed in the planetary gear guide slot (12_2) of the first fixed plate (12a), rotates, and moves while being constrained by the planetary gear guide slot (12_2).

[0127] 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.

[0128] The outer sleeve (121b), left fixing screw (122b), and right fixing screw (123b) constituting the gear sleeve (120b) according to the second embodiment of the present invention have the same shape and function as the outer sleeve (121), left fixing screw (122), and right fixing screw (123) constituting the gear sleeve (120) according to the first embodiment of the present invention.

[0129] The bidirectional damper (130b) of the planetary gear (11b) is configured to include a main spring (131b) (a in FIG. 12i), a left support plate (132b) (b in FIG. 12i), and a right support plate (133b) (c in FIG. 12i), and dampens the left and right movement of the gear sleeve (120b) to limit it within a certain range.

[0130] The main spring (131b) constituting the bidirectional buffer (130b) according to the second embodiment of the present invention can be implemented as a coil spring that surrounds the left pin (112b) extended into the outer sleeve (121b), unlike the main spring (131) constituting the bidirectional buffer (130) according to the first embodiment of the present invention which is received inside the inner sleeve (111). (i.e., a shape located between the inner diameter of the outer sleeve (121b) constituting the gear sleeve (120b) and the outer diameter of the left pin (112b).

[0131] The left support plate (132b) is supported by the left pin (112b) to the left and cannot move further, but is pressed by the left fixing screw (122b) to the right and can move up to a certain range (approximately 1 / 2 pitch) while pressing the main spring (131b) located on the outer circumference of the left pin (112b).

[0132] The right support plate (133b) is supported to the right by the compression rod (141b) described below and cannot move further, but to the left it is pressed by the compression rod (141b) and can move up to a certain range (approximately 1 / 2 pitch) while pressing the main spring (131b) located on the outer circumference of the left pin (112b).

[0133] 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 radius of rotation is large relative to the drive shaft (1), and increases the pressure of the main spring (131b) when the radius of rotation is small.

[0134] The compression rod (141b) is in the shape of a cylinder with a screw formed on its inner circumference and is screw-coupled 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).

[0135] 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 as a single unit.

[0136] One end of the pressure regulating pin (142b) is integrally connected with the right pin (113b) and rotates together with the right pin (113b). Additionally, the other end of the pressure regulating pin (142b) has a screw formed on its outer circumference and is screw-coupled with the inner circumference of the compression rod (141b). Between the one end and the other end of the pressure regulating pin (142b), a regulating projection (142b_1) is formed on its outer circumference. The leftward movement pressure of the gear sleeve (120b) is transmitted from the right fixing screw (123b) to the regulating projection (142b_1) through the rotation assist ring (161b) (Fig. 121), thereby moving the pressure regulating pin (142b) to the left.

[0137] The rotation guide (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 within a fine range in response to the left-right movement pressure of the gear sleeve (120b), and provides auxiliary cushioning for the left-right movement of the gear sleeve (120b).

[0138] The left rotational pressure ring (152b) is coupled to the gear sleeve (120b) and rotates synchronously, and has a one end portion that receives rightward movement pressure from the gear sleeve (120b) and a other end portion formed with a side groove (152b_1).

[0139] The left support ring (153b) is positioned to the left of the auxiliary spring (151b) and is installed to be movable 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 rotational pressure ring (152b) is formed at one end, and the other end supports the auxiliary spring (151b).

[0140] The right rotational pressure ring (155b) is coupled to the gear sleeve (120b) and rotates synchronously, and has one end portion that receives leftward movement pressure from the gear sleeve (120) and the other end portion formed with a side groove (155 / b_1).

[0141] The right support ring (155 / b) is positioned to the right of the auxiliary spring (151b) and is installed to be movable only to the left, and a side key (154b_1) corresponding to the side groove (155b_1) of the right rotational pressure ring (155b) is formed at one end, and the other end supports the auxiliary spring (151b).

[0142] The left rotational pressure ring (152b) and the right rotational pressure ring (154b) of the rotational inducer (150b) rotate in mutually opposite directions within a fine range in response to the moving pressure from the gear sleeve (120b), thereby rotating the rotationally synchronized gear sleeve (120b).

[0143] The rotation assist ring (161b) according to the second embodiment of the present invention has the same shape and function as the rotation assist ring (161) according to the first embodiment of the present invention.

[0144] The present invention has been described above with reference to preferred embodiments. Those skilled in the art will understand that the present invention may be embodied in modified forms without departing from the essential characteristics of the invention. Therefore, the disclosed embodiments should be considered in an illustrative rather than a restrictive sense. The scope of the invention is defined by the claims, not by the foregoing description, and all variations within the scope of equivalents should be interpreted as being included in the invention. Explanation of the symbols

[0145] 1: Drive shaft 2: Driven shaft 1_1 : Drive shaft groove 2_1 : Driven shaft groove 10, 10b: Drive gear assembly 20, 20b: Driven gear assembly 11, 21, 11b, 21b : Planetary gear 12_1 : Connecting key 12, 12a, 12b, 22, 22a, 22b : Fixing plate 12_2, 12a_2, 12b_2, 22_2, 22a_2 : Planetary gear guide slot 12a_3, 22a_3 : Guide gear for spring pressure adjustment 13, 13a, 13b, 23, 23a, 23b: Turntable 13_1, 23_1 : Screw 13_2 : Rotating arm through groove 14, 24 : Rotating arm 14_1 : Rotating arm first section 14_2 : Rotating arm end 15, 25 : Angle support plate 15_1 : Normal Slot 30 : Belt 30_1 : Belt gear 31 : Gear piece 32 : Twisted steel wire 33 : Tension bolt 34 : Support plate 34_1 : Steel line receiving groove 34_2 : Bolt hole 35 : Cover plate (32) 40, 40b: Speed ​​controller 41, 41a, 41b, 41c, 41d: Sleeve 42 : Bearing 43, 43b : Interlocking control unit 43_1, 43b_1 : Interlocking control arm 43_2, 43b_2 : Inclined gear 43b_3 : Guide slot 44 : Hydraulic device 45: Piston 46, 46b: Pressure position adjuster 46_1, 46b_1 : Guide gear 46_2, 46b_2 : Control rod 46_3 : Roller groove 46b_4 : Rotating arm 46b_5 : Interlocking control bracket restraint pin 46b_7 : Rotation restraint pin 46b_8 : Key 48, 48b : Roller device 48_1, 48b_1 : Support 48_2, 48b_2 : Roller arm 48_3, 48b_3 : Roller 48_4, 48b_4 : Inclined gear 48b_5 : Roller hinge extension rod 110, 110b : Main body 111 : Inner sleeve 112. 112b : Left pin 112_1, 112b_1 : Connecting projection 113, 113b: Right pin 113_1, 113b_1: Spring pressure adjustment gear 120, 120b: Gear sleeve 121, 121b: Outer sleeve 121_1, 121b_1: Planetary gear gears 122, 122b: Left-hand locking screw 123, 123b: Right fixing screw 130, 130b: Bidirectional buffer 131, 131b: Main spring 132, 132b: Left support plate 133: Right support plate, 133b 140, 140b: Spring pressure regulator 141, 141b: Compression rod 142, 142b: Pressure regulating pin 142_1, 142b_1: Adjustment projection 150, 150b: Rotation inducer 151, 151b: Auxiliary spring 152, 152b: Left rotational pressure ring 153, 153b: Left support ring 154, 154b: Right support ring 155, 155b: Right rotation pressure ring 152_1, 155_1 : Side sloped groove 152b_1, 155b_1 : Side groove 153_1. 154_1 : Side slope key 153b_1, 154b_1 : Side key 161, 161b: Rotation assist ring 161_1 : Outer key 161_2 : Inner key

Claims

Claim 1 A belt-type gear transmission that transmits rotational force of a drive shaft to a driven shaft 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 its inner surface and connecting the drive gear assembly and the driven gear assembly to transmit rotational force of the drive shaft to the driven shaft; and a transmission controller that controls the transmission such that the increase or decrease in the rotational radius of the drive gear assembly is coupled in a manner opposite to the increase or decrease in the rotational radius of the driven gear assembly. The transmission controller comprises: first and second sleeves, each installed on the drive shaft, which slide and reciprocate in an axial direction parallel to the drive shaft and have screw threads formed on their outer circumference; third and fourth sleeves, each installed on the driven shaft, which slide and reciprocate in the axial direction and have screw threads formed on their outer circumference; and a control plate having an H shape and coupled to the first to fourth sleeves by bearings at each of the four corners. A hydraulic device comprising a piston that reciprocates the interlocking control unit in the axial direction; wherein the screw threads formed on the outer circumference of the first and second sleeves and the third and fourth sleeves are formed in mutually opposite directions, and further comprising a pressure position adjuster that controls the hydraulic device to move toward the side with a relatively larger radius of rotation between the driving gear assembly and the driven gear assembly to apply pressure to the interlocking control unit, wherein the pressure position adjuster comprises: a guide gear installed in a direction parallel to the axial direction; a guide slot formed on the interlocking control unit in a direction perpendicular to the axial direction; a control rod having one end fixedly coupled to the piston and reciprocating in the axial direction; a rotating gear hinged to the other end of the control rod by a rotation restraint pin and meshing with the guide gear; and a rotating gear having one end hinged to the other end of the control rod by the rotation restraint pin and rotated while being restrained to the rotation of the rotating gear by a key of the rotation restraint pin, and the other end restrained in the axial direction by the guide slot and maintained to be movable in a direction perpendicular to the axial direction. A belt-type gear transmission characterized by including a rotating arm. Claim 2 A belt-type gear transmission according to claim 1, comprising: first and second interlocking control arm, each having one end fixedly coupled to the interlocking control arm and the other end equipped with an inclined gear; first and second supports installed on both sides between a driving gear assembly and a driven gear assembly; first and second roller hinge extension rods, each having one end equipped with an inclined gear that meshes with the inclined gear of the first and second interlocking control arm; and first and second roller arms, each hinge-coupled to the first and second supports and rotating by an inclined gear installed by extending from the first and second roller hinge extension rods coupled to one end, while pressing a belt by a roller provided at the other end; and further comprising a roller device in which the first and second roller arms rotate within a certain range by the inclined gear of the first and second roller hinge extension rods corresponding to the linear reciprocating motion of the interlocking control arm. Claim 3 A belt-type gear transmission characterized in that, in paragraph 2, the first and second roller arms each rotate toward the side with the smaller radius of rotation between the driving gear assembly and the driven gear assembly to press the belt.

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