Planetary transmission

Abstract

To provide a planetary transmission having a wide adjustment range of a transmission gear ratio.SOLUTION: A planetary roller of a planetary transmission includes: an input side roller part which contacts with each of a sun roller and a guide ring; and an output side roller part which is disposed so as to be arranged side by side with the input side roller part in a planetary axis direction of the planetary roller and contacts with an inner peripheral surface of the output ring. One of the input side roller part and the output side roller part has a designated taper outer peripheral surface inclining relative to the planetary axis direction. A transmission gear ratio adjustment mechanism is configured to change an output side contact position where the designated taper outer peripheral surface contacts with an inner peripheral surface of the output ring or an input side contact position where the designated taper outer peripheral surface contacts with an inner peripheral surface of the guide ring in an axial direction of an input shaft.SELECTED DRAWING: Figure 1A

Description

[Technical field]

[0001] SUMMARY The present disclosure relates to planetary transmissions configured to adjust a transmission ratio, which is the ratio of the angular velocity of an output shaft to the angular velocity of an input shaft. [Background technology]

[0002] There is known a planetary transmission capable of adjusting the gear ratio between an input shaft and an output shaft. For example, the planetary transmission disclosed in Patent Document 1 includes a sun roller supported by the input shaft, planetary rollers rolling on the outer peripheral surface of the sun roller, and an output ring with which the planetary rollers abut from the inside and which is formed integrally with the output shaft. Furthermore, the planetary rollers include tapered portions that abut from the inside against a speed change ring, which is a component of the planetary transmission. The speed change ratio is adjusted by displacing the speed change ring in the axial direction. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 5028264 Summary of the Invention [Problem to be solved by the invention]

[0004] It is preferable that the adjustment range of the gear ratio is wide.

[0005] An object of the present disclosure is to provide a planetary transmission device with a wide adjustment range for the gear ratio. [Means for solving the problem]

[0006] A planetary transmission according to at least one embodiment of the present disclosure includes: An input shaft and an output shaft arranged coaxially with each other; a sun roller supported by the input shaft; a guide ring located on an outer circumferential side of the sun roller and surrounding the input shaft; a planetary roller sandwiched between the sun roller and the guide ring; an output ring that contacts the planetary rollers from an outer circumferential side and is connected to the output shaft; a gear ratio adjusting mechanism for adjusting a gear ratio, which is a ratio of an angular velocity of the output shaft to an angular velocity of the input shaft; Equipped with The planetary roller is an input side roller portion that contacts the sun roller and the guide ring; an output side roller portion arranged to be aligned with the input side roller portion in a planetary axis direction of the planetary rollers and abutting against an inner peripheral surface of the output ring; Including, Either the input side roller portion or the output side roller portion has a specified tapered outer peripheral surface that is inclined with respect to the planetary axis direction, The gear ratio adjustment mechanism is configured to change an output side abutment position where the specified tapered outer peripheral surface abuts against the inner peripheral surface of the output ring, or an input side abutment position where the specified tapered outer peripheral surface abuts against the inner peripheral surface of the guide ring, in the axial direction of the input shaft. Effect of the Invention

[0007] According to the present disclosure, a planetary transmission device with a wide adjustment range for the gear ratio is provided. [Brief description of the drawings]

[0008] [Figure 1A] 1 is a schematic diagram of a planetary transmission according to a first embodiment. [Figure 1B] FIG. 6 is a schematic diagram of a planetary transmission according to a second embodiment. [Figure 1C] FIG. 11 is a schematic diagram of a planetary transmission according to a third embodiment. [Diagram 2] FIG. 4 is a schematic diagram showing a relationship between an outer diameter ratio and a gear ratio according to one embodiment. [Diagram 3] 13 is a schematic diagram of a biasing portion according to another embodiment. FIG. [Figure 4A] FIG. 2 is a schematic diagram of a biasing ring according to a first example. [Figure 4B]FIG. 11 is a schematic diagram of a biasing ring according to a second example. [Diagram 5] 13 is a schematic diagram of a biasing portion according to another embodiment. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] Hereinafter, some embodiments of the present disclosure will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of components described as the embodiments or shown in the drawings are merely illustrative examples and are not intended to limit the scope of the present disclosure. For example, expressions expressing relative or absolute configuration, such as "in a certain direction," "along a certain direction," "parallel," "orthogonal," "center," "concentric," or "coaxial," not only strictly express such a configuration, but also express a state in which there is a relative displacement with a tolerance or an angle or distance to the extent that the same function is obtained. For example, expressions indicating that things are in an equal state, such as "identical," "equal," and "homogeneous," not only indicate a state of strict equality, but also indicate a state in which there is a tolerance or a difference to the extent that the same function is obtained. For example, expressions describing shapes such as a rectangular shape or a cylindrical shape do not only refer to rectangular shapes, cylindrical shapes, etc. in the strict geometric sense, but also refer to shapes that include uneven portions, chamfered portions, etc., to the extent that the same effect is obtained. On the other hand, the expressions "comprise", "include", or "have" a certain element are not exclusive expressions excluding the presence of other elements. In addition, the same components are denoted by the same reference numerals and the description thereof may be omitted.

[0010] <Outline of Planetary Transmission 1> 1A to 1C show planetary transmissions 1A to 1C(1) according to several embodiments. Before describing the specific configuration of each embodiment in detail, the planetary transmission 1 will be outlined.

[0011] The planetary transmission 1 illustrated in FIGS. 1A to 1C includes an input shaft 2, an output shaft 3, and a housing 10 that rotatably supports the input shaft 2 and the output shaft 3. The input shaft 2 and the output shaft 3 are arranged coaxially with each other, and the axes of the input shaft 2 and the output shaft 3 correspond to the axis Ax of the planetary transmission 1. The housing 10 supports the input shaft 2 via bearings B1, B2, etc. (The support structure will be described in detail later.) The output shaft 3 is connected to an output side connecting holder 25, and a cylindrical portion 27 of the output side connecting holder 25 is connected to the housing 10 via a bearing B3. The output side connecting holder 25 is configured to rotate integrally with the output shaft 3 while being accommodated in the housing 10. The output shaft 3 is connected to an external device (not shown).

[0012] The rotation input to the input shaft 2 is transmitted to an external device via the output shaft 3, and the planetary transmission 1 is configured to make the angular velocity of the output shaft 3 different from the angular velocity of the input shaft 2. Furthermore, in this embodiment, the gear ratio, which is the ratio of the angular velocity of the output shaft 3 to the angular velocity of the input shaft 2, is adjusted by a gear ratio adjusting mechanism 30 of the planetary transmission 1 (the gear ratio adjusting mechanism 30 will be described in detail later).

[0013] In the following description, the axial direction of the input shaft 2 may be simply referred to as the "axial direction." The circumferential direction and radial direction based on the input shaft 2 may be simply referred to as the "circumferential direction" and the "radial direction," respectively. The "radial inner side" is the side approaching the axis Ax, and the "radial outer side" is the side moving away from the axis Ax. Since the input shaft 2 and the output shaft 3 are coaxially arranged, the "axial direction" is synonymous with the axial direction of the output shaft 3, and the "circumferential direction" and the "radial direction" are synonymous with the circumferential direction and the radial direction based on the output shaft 3, respectively. In the example of FIG. 1A to FIG. 1C, the output shaft 3 is arranged on one side of the "axial direction" with respect to the input shaft 2.

[0014] <Planetary transmission 1A(1) according to the first embodiment> Fig. 1A is a schematic diagram of a planetary transmission 1A according to a first embodiment. The planetary transmission 1A includes a sun roller 11A (11) supported by an input shaft 2, a guide ring 32A (32) located on the outer circumferential side of the sun roller 11A and surrounding the input shaft 2, and an output ring 15A (15) connected to a cylindrical portion 27 of an output side connection holder 25. The sun roller 11A, the guide ring 32A, and the output ring 15A are all housed in a housing 10. In the example of Fig. 1A, a sun outer circumferential surface 12A (12), which is the outer circumferential surface of the sun roller 11A, is a tapered surface inclined with respect to the axial direction.

[0015] The guide ring 32A is fixed to the inner wall surface of the housing 10. The inner peripheral surface of the guide ring 32A (32), that is, a guide ring inner peripheral surface 33A (33), is a tapered surface formed so that the inner diameter becomes smaller toward the other side in the axial direction. The output ring 15A is held in the cylindrical portion 27 so as to be displaceable in the axial direction. Also, the inner peripheral surface of the output ring 15A, that is, an output ring inner peripheral surface 16A (16), is formed so as to have approximately the same inner diameter regardless of the axial position.

[0016] Furthermore, the planetary transmission 1A includes a planetary roller unit 5A(5) including a planetary roller 6A(6) sandwiched between the sun roller 11A and the guide ring 32A. The planetary roller unit 5A further includes a pair of planetary carriers 39 arranged in the axial direction, and a planetary roller shaft 4A(4) supported by the pair of planetary carriers 39. Each planetary carrier 39 is rotatably supported by the input shaft 2. In the example of FIG. 1A, a bearing B1 is interposed between the planetary carrier 39 on the other side in the axial direction and the input shaft 2, and the planetary carrier 39 is further connected to the housing 10 via a bearing B2. A bearing (not shown) is also interposed between the planetary carrier 39 on one side in the axial direction and the input shaft 2. The planetary carrier 39 on one side in the axial direction is surrounded by a cylindrical portion 27 extending in the circumferential direction, and is connected to the output side connection holder 25 via a bearing B4.

[0017] The planetary roller shaft 4A extends at an angle to the axial direction, more specifically, extends radially outward as it approaches one side in the axial direction. The planetary roller shaft 4A supports the planetary roller 6A via at least one planetary bearing Bp.

[0018] In the following description, the axial direction of the planetary roller shaft 4A(4) may be referred to as the "planetary axial direction," and the radial direction based on the planetary roller shaft 4A(4) may be referred to as the "planetary radial direction." Additionally, the axis of the planetary roller shaft 4A(4) may be referred to as the "planetary axis Ap."

[0019] The planetary roller 6A includes an input side roller portion 7A (7) and an output side roller portion 8A (8) arranged side by side in the planetary axis direction. The input side roller portion 7A (7) abuts against the solar outer peripheral surface 12A (12) and the guide ring inner peripheral surface 33A (33). The output side roller portion 8A (8) abuts against the output ring inner peripheral surface 16A from the inside in the radial direction. In other words, the output ring inner peripheral surface 16A (16) abuts against the output side roller portion 8A from the outer peripheral side (outside in the radial direction). In the example of FIG. 1A, the input side roller portion 7A and the output side roller portion 8A are integrally formed of the same material, but the present disclosure is not limited to this. The input side roller portion 7A and the output side roller portion 8A may be formed separately from each other.

[0020] A plurality of planetary rotation mechanisms, each including a planetary roller 6A(6), a planetary roller shaft 4A(4), and a planetary bearing Bp, are arranged in the circumferential direction. In Fig. 1A, only a single planetary rotation mechanism is shown for the sake of simplicity, but another planetary mechanism is actually arranged within the area indicated by the two-dot chain line R1.

[0021] The operation of the planetary transmission 1A(1) is outlined as follows. When torque is input to the input shaft 2, the sun roller 11A(11) rotates integrally with the input shaft 2. The planetary roller 6A(6) rotates about the planetary roller shaft 4A(4) and also rotates about the input shaft 2 along the sun outer peripheral surface 12A(12) and the guide ring inner peripheral surface 33A. The rotational force of the planetary roller 6A rotates the output ring 15A together with the output side connecting holder 25, and torque is output from the output shaft 3 to an external device.

[0022] The gear ratio of the planetary transmission 1A will be described. The gear ratio (Gr) is the ratio of the angular velocity of the output shaft 3 to the angular velocity of the input shaft 2. The gear ratio (Gr) according to the first embodiment is defined by the following formula (1).

number

[0023] The symbols contained in formula (1) are defined below. R r1 is the distance in the planetary radial direction from a first contact position where the outer peripheral surface 71A (71) of the input side roller portion 7A contacts the inner peripheral surface 33A of the guide ring to the axis line Ax. Here, when surface contact occurs between the outer peripheral surface 71A (71) and the inner peripheral surface 33A of the guide ring, the central position in the planetary axis direction of the area where the surface contact occurs is defined as the first contact position. R r2 is the distance in the planetary radial direction from the second contact position where the output side roller portion 8A contacts the output ring inner peripheral surface 16A to the axis Ax. Here, when surface contact occurs between the output side roller portion 8A and the output ring inner peripheral surface 16, the central position in the planetary axial direction of the area where the surface contact occurs is defined as the second contact position. R p1 is the distance in the planetary radial direction from the third contact position where the outer peripheral surface 71A (71) of the input side roller portion 7A contacts the solar outer peripheral surface 12A to the planetary axis line Ap. Here, when surface contact occurs between the outer peripheral surface 71A and the solar outer peripheral surface 12A, the central position in the planetary axis direction of the area where the surface contact occurs is defined as the third contact position. R p2 is the distance in the planet radial direction from the second contact position to the planet axis Ap. R s1 is the outer diameter of the solar outer surface 12A. When the solar outer surface 12A is a tapered surface inclined with respect to the axial direction, the outer diameter of the central part of the solar outer surface 12A in the axial direction is R s1 It is defined as:

[0024] Continuing to refer to FIG. 1A, the description of the configuration of the planetary transmission 1A will be continued. Either the input side roller portion 7A (7) or the output side roller portion 8A (8) is formed with a prescribed tapered outer peripheral surface 18A (18). In the example of FIG. 1A, the prescribed tapered outer peripheral surface 18A is formed on the outer peripheral surface of the output side roller portion 8A, and the planetary roller shaft 4A is inclined so that the uppermost end of the prescribed tapered outer peripheral surface 18A extends parallel to the axial direction. The uppermost end of the prescribed tapered outer peripheral surface 18A abuts against the guide ring inner peripheral surface 33A. On the other hand, the input side roller portion 7A is formed in a cylindrical shape having approximately the same outer diameter regardless of the planetary axis direction position. In the example shown in FIG. 1, the maximum outer diameter of the prescribed tapered outer peripheral surface 18A is the same as the outer diameter of the outer peripheral surface 71A of the input side roller portion 7A. In other embodiments, the outer peripheral surface 71A of the input side roller portion 7A may also be formed in a tapered shape inclined with respect to the planetary axis direction. In this case, the outer circumferential surface 71A is a tapered outer circumferential surface different from the specified tapered outer circumferential surface 18A.

[0025] The planetary transmission 1A (1) further includes a gear ratio adjustment mechanism 30A (30) for adjusting the gear ratio. The planetary transmission 1A is configured to change an output side abutment position Po, which is the position where the specified tapered outer peripheral surface 18A abuts against the output ring inner peripheral surface 16A (16), in the axial direction. The output side abutment position Po according to the first embodiment is the same as the above-mentioned second abutment position.

[0026] The configuration of the gear ratio adjustment mechanism 30A will be described. The gear ratio adjustment mechanism 30A is held by the output side connecting holder 25, radially inward of the cylindrical portion 27. The gear ratio adjustment mechanism 30A includes an output ring connecting rod 35 connected to the output ring 15A (15), and an output side rod holding portion 36 connected to the output ring connecting rod 35. The output ring connecting rod 35 is configured to be displaced in the axial direction together with the output ring 15A (the specific configuration will be described later). As the axial position of the output ring 15A is displaced, the output side abutment position Po is displaced in the axial direction, and R in formula (1) p2 This allows the speed ratio adjustment mechanism 30A to adjust the speed ratio.

[0027] A configuration for displacing the output ring connecting rod 35 in the axial direction will be illustrated. As a first example, the output side rod holding part 36 has a ball screw arranged to axially penetrate the output side connection holder 25, and a screw part screwed to the ball screw. In this case, the screw part is connected to one end of the output ring connecting rod 35. The screw part moves along the ball screw while rotating, so that the output ring connecting rod 35 and the output ring 15A are displaced in the axial direction together. As a second example, the output side rod holding part 36 may be a hydraulic cylinder that houses a part of the output ring connecting rod 35. Even in this case, the output ring connecting rod 35 can be displaced in the axial direction.

[0028] As described above, the input side roller portion 7A(7) abuts against each of the sun roller 11A(11) and the guide ring 32A(32), the output side roller portion 8A(8) abuts against the inner peripheral surface 16A of the output ring, and the speed ratio adjustment mechanism 30A(30) is configured to change the output side abutment position Po in the axial direction. According to the above configuration, since the specified tapered outer peripheral surface 18A(18) is formed on the output side roller portion 8A(8), the outer diameters can be made different between the input side roller portion 7A and the output side roller portion 8A, and the planetary roller 6A(6) can be substantially configured as a two-stage structure. This makes it possible to provide a planetary transmission 1A(1) with a wide adjustment range for the speed ratio.

[0029] FIG. 2 is a schematic graph showing the relationship between the outer diameter ratio of the planetary roller 6A (6) and the speed ratio. The outer diameter ratio shown on the horizontal axis of the graph is a value obtained by dividing the outer diameter of the output side roller portion 8A (more specifically, the outer diameter of the specified tapered outer circumferential surface 18A at the output side abutment position Po) by the outer diameter of the input side roller portion 7A. The speed ratio specified in the graph can be calculated based on the above-mentioned formula (1). As shown in the graph, when the outer diameter ratio is changed in the range of 0.7 to 1.0, the speed ratio can be adjusted in the range of approximately 0 to 400, and a wide adjustment range of the speed ratio is realized. On the other hand, when the speed ratio of the configuration adopted in the above-mentioned Patent Publication No. 5028264 (hereinafter referred to as the conventional configuration) is expressed by a formula, R shown in formula (1) is p1 , R p2 Since the planetary transmission 1A does not include the planetary rollers, the gear ratio is inevitably much smaller than that of the planetary transmission 1A. To achieve the same gear ratio as the planetary transmission 1A, the conventional configuration requires, for example, a three-stage planetary roller structure, which may lead to an increase in size. In this regard, the planetary transmission 1A(1) of the present disclosure is capable of achieving a large gear ratio with a compact size.

[0030] Furthermore, according to a configuration in which the gear ratio adjustment mechanism 30A includes the output ring connecting rod 35, the output ring connecting rod 35 is displaced in the axial direction together with the output ring 15A (15), whereby the output side abutment position Po is changed in the axial direction, and the gear ratio can be adjusted.

[0031] The description of the configuration of the planetary transmission 1A will be continued with reference to FIG. 1A. The planetary transmission 1A further includes a contact roller 21A (21) that contacts the output side roller portion 8A (8) from the inside in the radial direction. In the example of FIG. 1A, the contact roller 21A contacts the specified tapered outer circumferential surface 18A of the output side roller portion 8A from the inside in the radial direction. The contact roller 21A (21) is rotatably provided on the input shaft 2. More specifically, a bearing (not shown) is interposed between the contact roller 21A (21) and the input shaft 2. When the planetary roller 6A (6) rotates around the input shaft 2, the contact roller 21A (21) rotates following the output side roller portion 8A.

[0032] Furthermore, the planetary transmission 1A further includes a biasing portion 50A (50) for biasing the output ring 15A (15) radially inward. In the embodiment illustrated in FIG. 1A, the biasing portion 50A includes the above-mentioned bearing B3. The bearing B3 is fitted into a fitting hole 41 formed between the housing 10 and the cylindrical portion 27 of the output side connection holder 25, and is pressed against the outer circumferential surface 27a of the cylindrical portion 27. In other words, the bearing B3 biases the output ring 15A radially inward via the cylindrical portion 27. At least a part of the axial range in which the bearing B3 is arranged is included in the axial range in which the output side abutment position Po can be displaced.

[0033] The pressing structure of the bearing B3 is realized by fitting the bearing B3 into the fitting hole 41 through shrink fitting or cold fitting. The shrink fitting process includes a step of increasing the inner diameter of the fitting hole 41 by heating the housing 10, a step of fitting the bearing B3 in a loose fit state into the fitting hole 41 with the increased inner diameter, and a step of cooling the housing 10 to reduce the inner diameter of the fitting hole 41. A description of the fitting process through cold fitting will be omitted.

[0034] According to the configuration in which the planetary transmission 1A(1) includes the contact roller 21A(21) and the biasing portion 50A(50), the output side roller portion 8A(8) can be pressed against the inner peripheral surface 16A(16) of the output ring. This can prevent slippage between the output side roller portion 8A(8) and the output ring 15A(15), and can efficiently transmit torque from the output side roller portion 8A(8) to the output ring 15A(15). Furthermore, according to the configuration in which the biasing portion 50A(50) includes the bearing B3, the bearing B3 has both a function of rotatably holding the output side connection holder 25 and a function of biasing the output ring 15A(15) radially inward. This can simplify the configuration of the planetary transmission 1A(1).

[0035] The description of the configuration of the planetary transmission 1A will be continued with reference to FIG. 1A. The specified tapered outer peripheral surface 18A formed on the output side roller portion 8A is inclined so that the outer diameter becomes smaller toward one side in the axial direction. In addition, the contact outer peripheral surface 22A of the contact roller 21A is configured so that the outer diameter becomes larger toward one side in the axial direction. Furthermore, the outer peripheral surface 71A (71) of the input side roller portion 7A is inclined so that it becomes radially outward toward one side in the axial direction, and the solar outer peripheral surface 12A is a tapered surface inclined so that the outer diameter becomes larger toward one side in the axial direction. The maximum outer diameter of the solar outer peripheral surface 12A is smaller than the minimum outer diameter of the contact roller 21A. In addition, the sun roller 11A and the contact roller 21A are arranged to be aligned in the axial direction with a gap therebetween.

[0036] According to the above configuration, the force transmitted from the specified tapered outer peripheral surface 18A(18) of the output side roller portion 8A(8) to the contact roller 21A is directed to one side in the axial direction (arrow F A ), and the force transmitted from the outer peripheral surface 71A of the input roller portion 7A(7) to the solar outer peripheral surface 12A(12) is directed to one side in the axial direction (arrow F A ) This makes it possible to reduce the load applied to the input shaft 2, thereby realizing a planetary transmission 1A(1) that makes it easy to input torque to the input shaft 2.

[0037] <Planetary transmission 1B(1) according to the second embodiment> Fig. 1B is a schematic diagram of a planetary transmission 1B according to a second embodiment. In Fig. 1B, the same components as those in Fig. 1A are given the same reference numerals, and the description of the components may be simplified or omitted below. For example, the gear ratio adjustment mechanism 30A and the output ring 15A illustrated in Fig. 1B are the same as those illustrated in Fig. 1A, and the description thereof will be omitted below.

[0038] The planetary transmission 1B(1) includes a planetary roller unit 5B(5). The planetary roller shaft 4B(4) of the planetary roller unit 5B extends radially outward toward the other side in the axial direction. The planetary roller 6B(6) includes an input roller portion 7B(7) and an output roller portion 8B(8). A prescribed tapered outer peripheral surface 18B(18) inclined with respect to the planetary axis direction is formed on the output roller portion 8B, and the input roller portion 7B is formed in a cylindrical shape having substantially the same outer diameter regardless of the position in the planetary axis direction. The guide ring 32B(32) is fixed to the housing 10, and the guide ring inner peripheral surface 33B of the guide ring 32B abuts against the outer peripheral surface 71B(71) of the input roller portion 7B. The guide ring inner peripheral surface 33B is a tapered surface formed so that the inner diameter becomes larger toward the other side in the axial direction.

[0039] In addition, for the sake of simplifying the drawing, the planetary rotation mechanism including the planetary roller 6B, the planetary roller shaft 4B, and the planetary bearing Bp is actually arranged within the area indicated by the dashed double-dashed line R2, but is omitted from FIG. 1B.

[0040] The prescribed tapered outer peripheral surface 18B is inclined so that the outer diameter becomes smaller toward the other side in the axial direction. The contact outer peripheral surface 22B (22) of the contact roller 21B (21) included in the planetary transmission 1B (1) is a tapered surface inclined so that the outer diameter becomes larger toward the other side in the axial direction. The outer peripheral surface 71B (71) of the input side roller portion 7B is inclined so that the outer diameter becomes larger toward the outside in the radial direction toward the other side in the axial direction. The sun outer peripheral surface 12B (12) of the sun roller 11B (11) is a tapered surface inclined so that the outer diameter becomes larger toward the other side in the axial direction. The minimum outer diameter of the sun outer peripheral surface 12B is larger than the maximum outer diameter of the contact roller 21B.

[0041] According to the above configuration, the force transmitted from the specified tapered outer peripheral surface 18B(18) of the output side roller portion 8B(8) to the contact roller 21B(21) is directed toward the other side in the axial direction (arrow F B), the force transmitted from the outer peripheral surface 71B of the input side roller portion 7B(7) to the solar outer peripheral surface 12B(12) is directed to the other side in the axial direction (arrow N B ). This makes it possible to reduce the load applied to the output shaft 3. Generally, the load applied to the output shaft 3 from an external device is greater than the load applied to the input shaft 2. With this configuration, by reducing the load applied to the output shaft 3, the loads applied to the input shaft 2 and the output shaft 3 can be equalized.

[0042] The gear ratio of the planetary transmission 1B is determined by the above-mentioned formula (1). As with the planetary transmission 1A, the planetary transmission 1B also realizes a wide range of adjustment for the gear ratio. Here, detailed explanations are omitted to avoid duplication.

[0043] <Planetary transmission 1C(1) according to the third embodiment> Fig. 1C is a schematic diagram of a planetary transmission 1C(1) according to a third embodiment. In Fig. 1C, the same components as those in Fig. 1A are given the same reference numerals, and the description of the components may be simplified or omitted below. For example, the planetary roller shaft 4A illustrated in Fig. 1C is the same as that illustrated in Fig. 1A, and the description thereof will be simplified below.

[0044] The planetary transmission 1C(1) includes a planetary roller unit 5C(5). The planetary roller unit 5C includes the planetary roller shaft 4A(4) and the planetary roller 6C supported by the planetary roller shaft 4A via the planetary bearing Bp. The planetary roller 6C(6) includes an input side roller portion 7C(7) and an output side roller portion 8C(8). A prescribed tapered outer peripheral surface 18C(18) inclined with respect to the planetary axis direction is formed on the input side roller portion 7C and abuts against the sun outer peripheral surface 12C(12) of the sun roller 11C(11). The output side roller portion 8C is formed in a cylindrical shape having approximately the same outer diameter regardless of the position in the planetary axis direction. The outer peripheral surface 72C(72) of the output side roller portion 8C abuts against the abutment outer peripheral surface 22C(22) of the abutment roller 21C(21) and also abuts against the output ring inner peripheral surface 16C of the output ring 15C.

[0045] In addition, for the sake of simplifying the drawing, the planetary rotation mechanism including the planetary roller 6C, the planetary roller shaft 4A, and the planetary bearing Bp is actually arranged within the area indicated by the dashed double-dashed line R3, but is omitted from FIG. 1C.

[0046] The planetary rollers 6C are arranged so that the uppermost end of the specified tapered outer peripheral surface 18C extends in the axial direction. The guide ring 32C (32) is cylindrical and has a substantially constant inner diameter regardless of the axial position, and the guide ring inner peripheral surface 33C (33) of the guide ring 32C abuts against the uppermost end of the specified tapered outer peripheral surface 18C. The guide ring 32C is held by the housing 10 so as to be displaceable in the axial direction. The outer peripheral surface 72C (72) of the output side roller portion 8C is inclined so as to move radially outward toward one side in the axial direction. The output ring inner peripheral surface 16C (16) that abuts against the outer peripheral surface 72C is a tapered surface whose inner diameter becomes larger toward one side in the axial direction.

[0047] The outline of the operation of the planetary transmission 1C is similar to that of the planetary transmission 1A described above. The gear ratio (Gr) of the planetary transmission 1C is defined by the following formula (2).

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[0048] In formula (2), R r2 , R p1 , R p2 , R s1 The dimensions of each of the above are as described above. R r3 is the distance in the planetary radial direction from the fourth contact position where the specified tapered outer peripheral surface 18C contacts the guide ring inner peripheral surface 33C (33) to the axis Ax. Here, when surface contact occurs between the specified tapered outer peripheral surface 18C and the guide ring inner peripheral surface 33C, the central position in the planetary axial direction of the area where the surface contact occurs is defined as the fourth contact position. R p3 is the distance in the planet radial direction from the fourth contact position to the planet axis Ap.

[0049] The speed ratio adjustment mechanism 30C(30) of the planetary transmission 1C(1) is configured to change the input side contact position Pi, which is the position where the guide ring inner peripheral surface 33C contacts the specified tapered outer peripheral surface 18C, in the axial direction. The input side contact position Pi is the fourth contact position described above.

[0050] The configuration of the gear ratio adjustment mechanism 30C will be described. The gear ratio adjustment mechanism 30C is held by the housing 10. The gear ratio adjustment mechanism 30C includes a guide ring connecting rod 37 that is connected to the guide ring 32C (32) and an input side connecting holder 38 that is connected to the housing 10. The guide ring connecting rod 37 is configured to be displaced in the axial direction together with the guide ring 32C. As the axial position of the guide ring 32C is displaced, the input side abutment position Pi is displaced in the axial direction, and R in formula (1) r3 and R p3 This allows the gear ratio adjustment mechanism 30C to adjust the gear ratio.

[0051] The input side connecting holder 38 may be a mechanism including a ball screw and a screw-threaded portion. In this case, the ball screw is disposed so as to penetrate the housing 10 in the axial direction, and the screw-threaded portion that screws into the ball screw is connected to the guide ring connecting rod 37. Alternatively, the input side connecting holder 38 may be a hydraulic cylinder that houses a portion of the guide ring connecting rod 37.

[0052] According to the above configuration, since the specified tapered outer peripheral surface 18C(18) is formed on the input roller portion 7C(7), the outer diameter can be made different between the input roller portion 7C and the output roller portion 8C, and the planetary roller 6C(6) can be substantially made into a two-stage structure. This makes it possible to provide a planetary speed change device 1C(1) with a wide range of adjustment for the speed change ratio.

[0053] Furthermore, according to a configuration in which the gear ratio adjustment mechanism 30C includes the guide ring connecting rod 37, the guide ring connecting rod 37 is displaced in the axial direction together with the guide ring 32C (32), whereby the input side abutment position Pi is changed in the axial direction, and the gear ratio can be adjusted.

[0054] In the example of FIG. 1C, the minimum outer diameter of the specified tapered outer peripheral surface 18C of the input side roller portion 7C is smaller than the outer diameter of the output side roller portion 8C. In this example, a step portion 99 is formed between a small diameter portion 181, which is the portion of the specified tapered outer peripheral surface 18C with the smallest outer diameter, and the outer peripheral surface 72C (72) of the output side roller portion 8C. The guide ring 32C is capable of being displaced in the axial direction up to the axial position where the guide ring inner peripheral surface 33C abuts against the outer peripheral surface of the small diameter portion 181. As a result, in the process of changing the axial position of the input side abutment position Pi, the "R r2 ·R p3 -R p2 ·R r3 " can be switched from a positive value to a negative value. In other words, the gear ratio can be switched from a positive value to a negative value. Since it becomes possible to change the direction of rotation of the output shaft 3, the usability of the planetary transmission 1C(1) can be improved.

[0055] <Using portion 50B (50) according to another embodiment> Fig. 3 is a schematic diagram of a biasing portion 50B according to another embodiment. Fig. 3 illustrates the biasing portion 50B applied to the planetary transmission 1A(1), but the biasing portion 50B may be applied to the planetary transmissions 1B and 1C.

[0056] The urging portion 50B includes a urging ring 70 that abuts against the outer peripheral surface 27a of the cylindrical portion 27 of the output side connection holder 25. The urging ring 70 is configured to urge the outer peripheral surface 27a toward the output side roller portion 8A(8). At least a part of the axial range in which the urging ring 70 is disposed is included in the axial range in which the output side abutment position Po can be displaced. According to the above configuration, the urging ring 70 abuts against the outer peripheral surface 27a, so that the output ring inner peripheral surface 16A(16) can be pressed against the output side roller portion 8A(8). This makes it possible to suppress the occurrence of slippage between the output side roller portion 8A(8) and the output ring 15A, and to efficiently transmit torque from the output side roller portion 8A to the output ring 15A.

[0057] A specific structure of the urging ring 70 will be described with reference to Figures 4A and 4B. Figure 4A is a schematic diagram of a urging ring 70A (70) according to a first example. Figure 4B is a schematic diagram of a urging ring 70B (70) according to a second example.

[0058] As shown in FIG. 4A, in the first example, the outer peripheral surface 27a of the cylindrical portion 27 has a plurality of teeth 28 arranged in the circumferential direction. The plurality of teeth 28 are uneven portions that extend continuously over the entire circumferential length of the outer peripheral surface 27a. The urging ring 70A includes an elastic belt 73 having a plurality of belt teeth 74 that mesh with the plurality of teeth 28, respectively. The elastic belt 73 is wound around the outer peripheral surface 27a in a state where it is elastically deformed so that its length in the circumferential direction is increased. The elastic belt 73 is in close contact with the outer peripheral surface 27a over the entire circumferential length of the cylindrical portion 27.

[0059] The elastic belt 73 biases the cylindrical portion 27 radially inward. This allows the output ring inner circumferential surface 16A (16) to press against the output side roller portion 8A (see FIG. 3). In addition, the belt teeth 74 mesh with the teeth 28 of the output side connection holder 25, respectively, so that the elastic belt 73 can be prevented from coming off the cylindrical portion 27 of the output side connection holder 25.

[0060] As shown in FIG. 4B, in the second example, the biasing ring 70B includes a first half ring 81 and a second half ring 82 each extending in an arc shape on the outer circumferential surface 27a of the cylindrical portion 27. The first half ring 81 and the second half ring 82 cooperate to form an O-ring shape when viewed in the axial direction. One end 81a of the first half ring 81 is connected to a first end 83 of the second half ring 82, and the other end 81b of the first half ring 81 is connected to a second end 84 of the second half ring 82. Fastening holes 87 and 88 are formed in the one end 81a and the other end 81b, respectively. The first end 83 is formed with a hole 83a that is open along the axial direction of the fastening hole 87 of the one end 81a. The second end 84 is formed with a hole 84a that is open along the axial direction of the fastening hole 88 of the other end 81b.

[0061] The urging ring 70B further includes a first fastening member 91 fastening one end 81a to the first end 83, and a second end 84 fastening the other end 81b to the second end 84. The fastening process of the first fastening member 91 includes a step of inserting the first fastening member 91 into the hole 83a, and a step of tightening the inserted first fastening member 91 into the fastening hole 87. Similarly, the fastening process of the second fastening member 92 includes a step of inserting the second fastening member 92 into the hole 84a, and a step of tightening the inserted second fastening member 92 into the fastening hole 88.

[0062] The first and second fastening members 91 and 92 fasten the first and second half rings 81 and 82 against the outer peripheral surface 27a of the output side connection holder 25. This allows the output ring inner peripheral surface 16A (16) to be pressed against the output side roller portion 8A (see FIG. 3). In addition, since the fastening force of each of the first and second fastening members 91 and 92 is adjustable, it is also possible to adjust the urging force applied to the output side roller portion 8A.

[0063] <Using portion 50C (50) according to another embodiment> Fig. 5 is a schematic diagram of a biasing unit 50C (50) according to another embodiment. The output side connection holder 25 illustrated in Fig. 5 includes a plurality of insertion holes 29 each of which is open to one side along the axial direction. The plurality of insertion holes 29 are arranged to be aligned along the circumferential direction. The biasing unit 50C includes a contraction ring member 110. The contraction ring member 110 has a plurality of insertion pins 112 which are inserted into the plurality of insertion holes 29, respectively, and an opposing ring 114 which is connected to each of the plurality of insertion pins 112 and faces the output side connection holder 25 in the axial direction.

[0064] The multiple insertion pins 112 respectively bias the multiple insertion holes 29 radially inward. The biasing structure of the insertion pins 112 is realized by fitting the insertion pins 112 into the insertion holes 29 through shrink fitting or cold fitting. The shrink fitting process includes a step of displacing the radial positions of the insertion holes 29 radially outward by heating the output side connection holder 25, a step of inserting the insertion pins 112 into the insertion holes 29 displaced radially outward, and a step of cooling the output side connection holder 25 to displace the radial positions of the insertion holes 29 radially inward. A description of the fitting process through cold fitting will be omitted.

[0065] According to the above configuration, the multiple insertion pins 112 urge the multiple insertion holes 29 radially inward, so that the cylindrical portion 27 of the output side connection holder 25 can urge the output side roller portion 8A radially inward. This allows the output ring inner circumferential surface 16A to be pressed against the output side roller portion 8A.

[0066] <Summary> The contents described in the above-mentioned embodiments can be understood, for example, as follows.

[0067] 1) A planetary transmission (1) according to at least one embodiment of the present disclosure, An input shaft (2) and an output shaft (3) arranged coaxially with each other; A sun roller (11) supported by the input shaft; a guide ring (32) located on the outer circumferential side of the sun roller and surrounding the input shaft; A planetary roller (6) sandwiched between the sun roller and the guide ring; an output ring (15) that contacts the planetary rollers from the outer circumferential side and is connected to the output shaft; a speed ratio adjustment mechanism (30) for adjusting a speed ratio, which is a ratio of the angular velocity of the output shaft to the angular velocity of the input shaft; Equipped with The planetary roller is an input side roller portion (7) that contacts the sun roller and the guide ring, an output side roller portion (8) arranged to be aligned with the input side roller portion in the planetary axis direction of the planetary roller and abutting against an inner peripheral surface (output ring inner peripheral surface 16) of the output ring; Including, Either the input side roller portion or the output side roller portion has a prescribed tapered outer peripheral surface (18) inclined with respect to the planetary axis direction, The gear ratio adjustment mechanism is configured to change an output side abutment position (Po) at which the specified tapered outer peripheral surface abuts against the inner peripheral surface of the output ring, or an input side abutment position (Pi) at which the specified tapered outer peripheral surface abuts against the inner peripheral surface of the guide ring (guide ring inner peripheral surface 33), in the axial direction of the input shaft.

[0068] According to the above configuration 1), the output side contact position or the input side contact position is changed in the axial direction of the input shaft to adjust the gear ratio. Since the specified tapered outer peripheral surface is formed on either the input side roller portion or the output side roller portion, the outer diameter can be made different between the input side roller portion and the output side roller portion, and the planetary roller can essentially have a two-stage structure. This makes it possible to provide a planetary transmission with a wide range of adjustment for the gear ratio.

[0069] 2) In some embodiments, the planetary transmission described in 1) above is The rotary shaft further includes a contact roller (21) that is rotatably mounted on the input shaft and contacts the output-side roller portion from the inside in a radial direction relative to the input shaft.

[0070] According to the above configuration 2), the output side roller portion can be pressed against the inner peripheral surface of the output ring, which makes it possible to prevent slippage between the output side roller portion and the output ring, and allows efficient transmission of torque from the output side roller portion to the output ring.

[0071] 3) In some embodiments, the planetary transmission according to 1) or 2) above is The rotor further includes a biasing portion (50) that biases the output ring inward in a radial direction relative to the input shaft.

[0072] According to the above configuration 3), the inner peripheral surface of the output ring can be pressed against the output side roller portion. This can prevent slippage between the output side roller portion and the output ring, and torque can be efficiently transmitted from the output side roller portion to the output ring. Furthermore, if a contact roller is provided, the output side roller portion is prevented from being displaced radially inward, and the biasing force can be sufficiently transmitted from the biasing portion to the output side roller portion via the output ring. This can increase the contact force between the output side roller portion and the output ring, and prevent slippage between the output side roller portion and the output ring.

[0073] 4) In some embodiments, the planetary transmission according to any one of 1) to 3) above, an output side connecting holder (25) connected to the output shaft, the output ring being held so as to be displaceable in the axial direction and the speed ratio adjustment mechanism being held; The specified tapered outer peripheral surface is formed on the output side roller portion, The transmission ratio adjustment mechanism includes an output ring connecting rod (35) connected to the output ring and configured to be displaced in the axial direction.

[0074] According to the above configuration 4), the output ring connecting rod is displaced in the axial direction together with the output ring, whereby the output side abutment position is changed in the axial direction, and the gear ratio can be adjusted.

[0075] 5) In some embodiments, the planetary transmission described in 4) above is a contact roller (21) that is rotatably supported by the input shaft and contacts the specified tapered outer peripheral surface of the output-side roller portion from a radially inner side relative to the input shaft, the output shaft is located on one side in the axial direction with respect to the input shaft, the specified tapered outer peripheral surface is inclined so that an outer diameter becomes smaller toward the one side in the axial direction, The outer circumferential contact surface (22) of the contact roller is inclined so that the outer diameter becomes larger toward the one side.

[0076] According to the configuration of 5) above, the force transmitted from the specified tapered outer peripheral surface of the output roller portion to the contact roller is directed to one side in the axial direction, thereby reducing the load applied to the input shaft, thereby realizing a planetary transmission that makes it easy to input torque to the input shaft.

[0077] 6) In some embodiments, the planetary transmission according to 4) or 5) above, the output shaft is located on one side in the axial direction with respect to the input shaft, an outer circumferential surface (71) of the input side roller portion is inclined toward the one side in the axial direction so as to be radially outward relative to the input shaft; The outer circumferential surface (12) of the sun roller is inclined so that the outer diameter becomes larger toward the one side in the axial direction.

[0078] According to the configuration of 6) above, the force transmitted from the outer circumferential surface of the input roller portion to the outer circumferential surface of the sun roller is directed to one side in the axial direction, thereby reducing the load on the input shaft. This realizes a planetary transmission that makes it easy to input torque to the input shaft.

[0079] 7) In some embodiments, the planetary transmission described in 4) above is a contact roller (21) that is rotatably supported by the input shaft and contacts the specified tapered outer peripheral surface of the output-side roller portion from a radially inner side relative to the input shaft, the output shaft is located on one side in the axial direction with respect to the input shaft, The specified tapered outer peripheral surface is inclined so that the outer diameter becomes smaller toward the other side in the axial direction, The outer circumferential contact surface (22) of the contact roller is inclined so that the outer diameter becomes larger toward the other side.

[0080] According to the configuration of 7) above, the force transmitted from the specified tapered outer peripheral surface of the output side roller portion to the contact roller is directed to the other side in the axial direction, so the load applied to the output shaft can be reduced. In general, the load applied to the output shaft from an external device driven by the torque output from the planetary speed change device is large. According to this configuration, the load applied to the output shaft can be reduced, so that the loads applied to the input shaft and the output shaft can be equalized.

[0081] 8) In some embodiments, the planetary transmission according to 4) or 5) above, the output shaft is located on one side in the axial direction with respect to the input shaft, the outer circumferential surface (71) of the input side roller portion is inclined toward the other side in the axial direction so as to be radially outward relative to the input shaft, The outer circumferential surface (12) of the sun roller is inclined so that the outer diameter becomes larger toward the other side in the axial direction.

[0082] According to the configuration of 8) above, the force transmitted from the outer circumferential surface of the input side roller portion to the outer circumferential surface of the sun roller is directed to the other side in the axial direction, so the load applied to the output shaft can be reduced. In general, the load applied to the output shaft from an external device driven by the torque output from the planetary transmission is large. According to this configuration, the load applied to the output shaft can be reduced, so that the loads applied to the input shaft and the output shaft can be equalized.

[0083] 9) In some embodiments, the planetary transmission according to any one of 1) to 3) above, a housing (10) that rotatably supports the input shaft and the output shaft, holds the guide ring in the axial direction, and holds the speed ratio adjustment mechanism; The specified tapered outer peripheral surface is formed on the input side roller portion, The speed ratio adjustment mechanism includes a guide ring connecting rod (37) connected to the guide ring and configured to be displaced in the axial direction.

[0084] According to the above configuration 9), the guide ring connecting rod is displaced in the axial direction together with the guide ring, whereby the input side contact position is changed in the axial direction, and the speed change ratio can be adjusted.

[0085] 10) In some embodiments, the planetary transmission according to 9) above, The minimum outer diameter of the specified tapered outer peripheral surface of the input side roller portion is smaller than the outer diameter of the output side roller portion.

[0086] According to the configuration of 10) above, the speed ratio can be changed between a positive value and a negative value, which makes it possible to change the rotation direction of the output shaft and improves the usability of the planetary transmission.

[0087] 11) In some embodiments, the planetary transmission according to 3) above, an output side connection holder (25) that is connected to the output ring and holds the output ring; a housing (10) for accommodating the output side connection holder and the output ring; Further equipped with The biasing portion is fitted into a fitting hole (41) formed in the housing and the output side connection holder, and includes a bearing (B3) that presses against the output side connection holder.

[0088] According to the above configuration 11), the bearing has both a function of rotatably holding the bearing output side connecting holder and a function of biasing the output ring radially inward, which simplifies the configuration of the planetary transmission.

[0089] 12) In some embodiments, the planetary transmission according to 3) above, an output side connection holder (25) connected to the output ring and holding the output ring; The urging portion includes a urging ring (70) that abuts against an outer circumferential surface (27a) of the output side connection holder and urges the outer circumferential surface toward the output side roller portion.

[0090] According to the above configuration 12), the biasing ring biases the outer circumferential surface of the output side connection holder, so that the inner circumferential surface of the output ring can be pressed against the output side roller portion.

[0091] 13) In some embodiments, the planetary transmission according to 12) above, The outer circumferential surface of the output side connection holder has a plurality of teeth (28) arranged in the circumferential direction of the output shaft, The biasing ring includes an elastic belt (73) having a plurality of belt teeth (74) that respectively mesh with the plurality of teeth, and which is wound around the outer peripheral surface of the output ring in a state in which it is elastically deformed so that its length in the circumferential direction is increased.

[0092] According to the above configuration 13), the inner peripheral surface of the output ring can be pressed against the output-side roller portion by the biasing force of the elastic belt. Also, since the multiple belt teeth mesh with the multiple teeth of the output-side connecting holder, the elastic belt can be prevented from coming off the output-side connecting holder.

[0093] 14) In some embodiments, the planetary transmission according to 13) above, The biasing ring is a first half ring (81) extending in an arc shape on the outer circumferential surface of the output side connection holder; a second half ring (82) extending in an arc shape on the outer circumferential surface between one end (81) of the first half ring and the other end (81b) of the first half ring; a first fastening member (91) that fastens the one end of the first half ring and a first end (83) of the second half ring; a second fastening member (92) that fastens the other end of the first half ring and the second end (84) of the second half ring; Includes.

[0094] According to the configuration of 14) above, the first and second fastening members are fastened to each other, so that the first and second half rings are pressed against the outer peripheral surface of the output side connection holder. This allows the inner peripheral surface of the output ring to be pressed against the output side roller portion. In addition, since the fastening force of each of the first and second fastening members is adjustable, it is also possible to adjust the urging force applied to the output side roller portion.

[0095] 15) In some embodiments, the planetary transmission described in 3) above is an output side connection holder (25) connected to the output ring and holding the output ring; The output side connection holder includes an insertion hole (29) that opens along the axial direction, The insertion hole is arranged in a plurality of holes along a circumferential direction of the output shaft, The biasing portion includes a contracting ring member (110); The contraction ring member is a plurality of insertion pins (112) that are inserted into the plurality of insertion holes, respectively, and bias the plurality of insertion holes toward the inside in the radial direction of the output shaft; an opposing ring (114) connected to each of the plurality of insertion pins and facing the output side connection holder in the axial direction; has.

[0096] According to the above configuration 15), the multiple insertion pins urge the multiple insertion holes inward in the radial direction, so that the output side connection holder can urge the output side roller portion inward in the radial direction, thereby allowing the inner peripheral surface of the output ring to press against the output side roller portion. [Explanation of symbols]

[0097] 1: Planetary transmission 2: Input shaft 3: Output shaft 4: Planetary roller shaft 5: Planetary roller unit 6: Planetary roller 7: Input roller section 8: Output roller section 10: Housing 11: Sun Roller 12: Solar outer surface 15: Output ring 16: Inner surface of output ring 18: Specified taper outer surface 21: Contact roller 22: Contact outer peripheral surface 25: Output side connection holder 27: Cylindrical section 27a: Outer surface 28: Teeth 29: Insertion hole 30: Gear ratio adjustment mechanism 32: Guide ring 32: Guide ring 33: Inner surface of guide ring 35: Output ring connecting rod 36: Output side rod holder 37: Guide ring connecting rod 38: Input side connection holder 39: Planet carrier 41: Fitting hole 50: Pressurizing section 70: Power ring 71,72:Outer surface 73: Elastic belt 74: Belt teeth 81: First Halfling 81a: One end 81b: Other end 82: Second Halfling 83:First end 83a,84a: hole 84:Second end 87,88: Fastening holes 91, 92: First fastening member 99: Step 110: Contraction ring member 112: Insert pin 114: Opposing ring 181: Small diameter part Ap: Planet axis Ax: Axis line B1, B2, B3, B4: Bearings Bp: Planetary bearing F A ,F B ,N B :Arrow Pi: Input side contact position Po: Output side contact position R1,R2,R3: Two-dot chain line

Claims

1. An input shaft and an output shaft arranged coaxially with each other; a sun roller supported by the input shaft; a guide ring located on an outer circumferential side of the sun roller and surrounding the input shaft; a planetary roller sandwiched between the sun roller and the guide ring; an output ring that contacts the planetary rollers from an outer circumferential side and is connected to the output shaft; a gear ratio adjusting mechanism for adjusting a gear ratio, which is a ratio of an angular velocity of the output shaft to an angular velocity of the input shaft; Equipped with The planetary roller is an input side roller portion that contacts the sun roller and the guide ring; an output side roller portion arranged to be aligned with the input side roller portion in a planetary axis direction of the planetary rollers and abutting against an inner peripheral surface of the output ring; Including, Either the input side roller portion or the output side roller portion has a specified tapered outer peripheral surface that is inclined with respect to the planetary axis direction, The speed ratio adjustment mechanism is configured to change an output-side abutment position where the specified tapered outer peripheral surface abuts against the inner peripheral surface of the output ring, or an input-side abutment position where the specified tapered outer peripheral surface abuts against the inner peripheral surface of the guide ring, in the axial direction of the input shaft. Planetary transmission.

2. a contact roller that is rotatably provided on the input shaft and contacts the output-side roller portion from the inside in a radial direction based on the input shaft; 2. The planetary transmission of claim 1.

3. The output ring further includes a biasing portion that biases the output ring inward in a radial direction relative to the input shaft.

3. A planetary transmission according to claim 1 or 2.

4. an output side connecting holder connected to the output shaft, the output ring being held displaceable in the axial direction and the speed ratio adjustment mechanism being held, The specified tapered outer peripheral surface is formed on the output side roller portion, The transmission ratio adjustment mechanism includes an output ring connecting rod connected to the output ring and configured to be displaced in the axial direction.

3. A planetary transmission according to claim 1 or 2.

5. a contact roller that is rotatably supported by the input shaft and contacts the specified tapered outer peripheral surface of the output-side roller portion from an inner side in a radial direction based on the input shaft, the output shaft is located on one side in the axial direction with respect to the input shaft, the specified tapered outer peripheral surface is inclined so that an outer diameter becomes smaller toward the one side in the axial direction, The contact outer circumferential surface of the contact roller is inclined so that the outer diameter becomes larger toward the one side.

5. The planetary transmission of claim 4.

6. the output shaft is located on one side in the axial direction with respect to the input shaft, an outer circumferential surface of the input side roller portion is inclined toward an outer side in a radial direction relative to the input shaft as the outer circumferential surface of the input side roller portion approaches the one side in the axial direction, The outer peripheral surface of the sun roller is inclined so that the outer diameter becomes larger toward the one side in the axial direction.

5. The planetary transmission of claim 4.

7. a contact roller that is rotatably supported by the input shaft and contacts the specified tapered outer peripheral surface of the output-side roller portion from an inner side in a radial direction based on the input shaft, the output shaft is located on one side in the axial direction with respect to the input shaft, The specified tapered outer peripheral surface is inclined so that the outer diameter becomes smaller toward the other side in the axial direction, The contact outer circumferential surface of the contact roller is inclined so that the outer diameter becomes larger toward the other side.

5. The planetary transmission of claim 4.

8. the output shaft is located on one side in the axial direction with respect to the input shaft, an outer circumferential surface of the input roller portion is inclined toward the other side in the axial direction so as to be radially outward relative to the input shaft; The outer peripheral surface of the sun roller is inclined so that the outer diameter becomes larger toward the other side in the axial direction.

5. The planetary transmission of claim 4.

9. a housing that rotatably supports the input shaft and the output shaft, holds the guide ring in the axial direction, and holds the gear ratio adjustment mechanism; The specified tapered outer peripheral surface is formed on the input side roller portion, The gear ratio adjustment mechanism includes a guide ring connecting rod connected to the guide ring and configured to be displaced in the axial direction.

3. A planetary transmission according to claim 1 or 2.

10. The minimum outer diameter of the specified tapered outer peripheral surface of the input side roller portion is smaller than the outer diameter of the output side roller portion.

10. The planetary transmission of claim 9.

11. an output side connection holder that is connected to the output ring and holds the output ring; a housing that accommodates the output side connection holder and the output ring; Further equipped with The biasing portion is fitted into a fitting hole formed in the housing and the output side connection holder, and includes a bearing that presses against the output side connection holder.

4. The planetary transmission of claim 3.

12. an output side connection holder that is connected to the output ring and holds the output ring; The biasing portion includes a biasing ring that contacts an outer circumferential surface of the output side connection holder and biases the outer circumferential surface toward the output side roller portion.

4. The planetary transmission of claim 3.

13. The outer circumferential surface of the output side connection holder has a plurality of teeth arranged in a circumferential direction of the output shaft, The urging ring includes an elastic belt having a plurality of belt teeth that mesh with the plurality of teeth, the elastic belt being wound around the outer circumferential surface of the output ring in a state in which the elastic belt is elastically deformed so as to increase in length in the circumferential direction.

13. The planetary transmission of claim 12.

14. The biasing ring is a first half ring extending in an arc shape on the outer circumferential surface of the output side connection holder; a second half ring extending in an arc shape on the outer circumferential surface between one end of the first half ring and the other end of the first half ring; a first fastening member that fastens the one end of the first half ring and a first end of the second half ring; a second fastening member fastening the other end of the first half ring and a second end of the second half ring; Includes 13. The planetary transmission of claim 12.

15. an output side connection holder that is connected to the output ring and holds the output ring; the output side connection holder includes an insertion hole that is open along the axial direction, The insertion hole is arranged in a plurality of holes along a circumferential direction of the output shaft, The biasing portion includes a contraction ring member. The contraction ring member is a plurality of insertion pins that are inserted into the plurality of insertion holes and bias the plurality of insertion holes toward an inner side in a radial direction of the output shaft; an opposing ring connected to each of the plurality of insertion pins and facing the output side connection holder in the axial direction; have 4. The planetary transmission of claim 3.

Images