JP2008524522A - Traction automatic adjustment planetary roller transmission - Google Patents

Abstract

A device capable of maintaining a traction state necessary for power transmission with high mechanical efficiency while maintaining a low level of noise and vibration.
The device includes a conical sun roller having a traction surface on a side wall, a traction track ring having a conical surface spaced concentrically from the sun roller, a traction surface, and a traction surface of the sun roller. And a plurality of conical planetary rollers located between the traction track ring and a planet carrier on which each planetary roller is rotatably mounted and spaced apart therefrom. As the transmission traction surface wears, the planetary roller can adjust its axial position and radial position between the traction surface of the sun roller and the traction track ring.
[Selection] Figure 1

Description

  The present invention relates to a technique used in designing and manufacturing a roller transmission, and more particularly to a traction (traction) automatic adjustment planetary roller transmission.

  It is well known that conventional power transmission systems incorporating gears present operational problems such as component malfunction, mechanical deficiencies, high noise and vibration levels. In particular, the latter two drawbacks are that the above-mentioned conventional power transmission system is a device, which is also a recreational vehicle, and the user does not like to hear noise or feel uncomfortable vibration. If incorporated, it is critical.

For this reason, the development of power transmission devices is currently focused on providing models with low noise and vibration levels. Nevertheless, it is noteworthy that transmission manufacturers demand that their products be highly efficient, compact and easy to manufacture.
In order to prevent noise, mechanical deficiencies, and vibrations, there are conventional planetary roller transmissions that operate on the principle of traction surfaces and do not require the use of crown gears. In particular, the transmission is usually composed of a sun member or roller having a traction surface, a traction track ring concentrically spaced from the sun member, and a sun roller and a traction track ring (annular traction track) separated from each other. It is composed of a plurality of planetary members or planetary rollers press-fitted in the gaps between them. More specifically, the sun roller is attached to the shaft that is the input shaft or the output shaft, and the planetary member or planetary roller is attached to the planet carrier that is mounted on another shaft that is axially parallel to the shaft to which the sun roller is attached. It is attached. With this configuration, if the power source connected to the shaft to which the sun roller is attached rotates the sun roller and the required traction state is realized, the planetary member or the planetary roller is also started. As the planetary member rotates, the output shaft starts at a different rotational speed than the input shaft so that power is transmitted and used as desired.

  It should be noted here that in this type of planetary roller transmission having a traction surface, in order to ensure the traction state required for the planetary member or planetary roller to operate, the sun roller and planetary member or planetary member are required. It is preferable that not only the traction surface of the roller but also the traction surface of the traction track ring has an inclination angle with respect to the transmission shaft, that is, has a conical surface.

  An example of a planetary roller type transmission device having this kind of conical traction surface is shown in Patent Document 1 below. This transmission device incorporates means for pressing the sun roller in the axial direction and arranging it between the planetary members to prevent sliding between the transmission traction surfaces. However, since these transmission devices are provided with cams for pressing such sun rollers in the axial direction, they require constant adjustment over time and guarantee proper operation of the transmission devices. There was a problem that had to be done.

  Another important aspect of this transmission is that the planetary member's traction surface is slightly bent to prevent sliding under low load conditions and to suppress the stress peaks between the traction surfaces. However, if this roller transmission is used, the traction surface will naturally wear out, so that the bent portion gradually disappears. As a result, it is clear that the transmission does not operate at the initial efficiency.

  Another planetary roller type transmission device having a conical traction surface is shown in Patent Document 2 below. One feature of this transmission is that it is a conical roller with an edge having a cone parallel to the axis of the roller transmission. The edge is further in contact with an outer ring that restrains the movement, and this element is the most important technical aspect of the transmission. With this configuration, the roller transmission is controlled in the lateral direction, that is, in the axial direction. However, this transmission is not immune from the traction surface wear process, and as shown in all of the above patents, sooner or later, the transmission must be disassembled to adjust and maintain its vast number of parts. .

  Finally, reference is made to a planetary roller transmission having a conical traction surface described in Patent Document 3 below. According to the teaching of the above document, in this transmission device, since the solar member is provided with two traction surfaces, two traction track rings and two sets of planetary rollers are provided. Of particular note is that the set is located between one of the traction tracks of the solar member and one of the traction track rings. Similarly, this roller transmission has the essential feature that all the rollers belonging to the first set are in contact with the planetary rollers belonging to the second set. Further, in this roller transmission, one traction track ring is rotatable, and the other traction track ring is fixed.

According to the description of the above document, the configuration of the roller transmission provided is as follows: (i) between the traction surface of the sun roller and the planetary roller belonging to one of the groups; (ii) the traction orbit ring; And (iii) preventing sliding or sliding of the traction section between the planetary rollers belonging to the pair and (iii) between the rollers belonging to both the pairs.
Nevertheless, this roller transmission is subject to a wear process, mainly a wear process on the traction surface, and its components will loosen over time, resulting in a traction state required for the operation of the roller transmission. Lost. Therefore, it is necessary to replace and adjust some components, particularly the planetary roller. Furthermore, since the roller transmission has two planetary roller systems, it is difficult to assemble and maintain multiple parts.

Another important aspect of planetary roller transmissions known to those skilled in the art is the use of elastohydrodynamic or traction lubricants inside the device to reach the traction coefficient required for starting the roller transmission. It was a must. However, such lubricants are very special, very expensive, and residue is generated which gradually changes the traction surface. In addition, elastohydrodynamic lubricants require high pressure in the vertical direction for power transmission, so such lubricants specify the manufacture of roller transmissions because of chemical erosion and mechanical resistance. Limiting the use of only materials, which increases the cost of the transmission.
US Pat. No. 4,846,008 Japanese Patent Laid-Open No. 06-280981 US Pat. No. 6,406,399

  In summary, planetary roller transmissions wear out on the traction surface, and over time, the traction state required for rotation of the planetary roller located between the sun roller and the traction orbital ring is lost, so It can be seen that some parts need to be replaced to adjust the roller transmission. Furthermore, most of the known planetary roller transmissions are provided with parts that are multiples of the split type, so that the roller transmissions are not compact in relation to their components.

  In view of the above, it is desired to suppress the disadvantages of the conventional planetary roller transmission device by realizing the following traction automatic adjustment planetary roller transmission device. That is, a conical sun roller having a bottom portion, a notch surface, and a traction surface of a side wall portion, a traction track ring having a conical surface concentrically spaced from the sun roller, a bottom portion, and a notch surface, A plurality of conical planetary rollers having a traction surface on the side wall, wherein the conical planetary rollers are disposed in an inclined state between the traction surface of the sun roller and the traction orbit ring, The traction surface of the planetary roller is in contact with the traction surface of the sun roller and the traction trajectory ring, and is provided with a conical planetary roller including a mounting shaft and spaced apart from each other at equal intervals around the sun roller. It is a self-adjusting planetary roller transmission.

  The traction automatic adjustment planetary roller transmission according to the present invention is provided with a planetary carrier, and each planetary roller is rotatably attached to the planetary carrier so as to be rotated away from the planetary roller by its attachment shaft. ing. In order to adjust the axial position and the radial position between the traction surface of the sun roller and the traction track ring as the traction surface of any of the planet rollers wears, each planet roller further includes a planet carrier. It is attached to be movable in the axial direction and the radial direction.

Further, the roller transmission device includes an input shaft mounted on the sun roller and parallel to the longitudinal axis of the roller transmission device, an output shaft mounted on the planet carrier and parallel to the input shaft, and the sun Axial load means for pressing the bottom of the roller, and a housing that covers the roller transmission, receives (receives) the input shaft, and projects the output shaft.
As the traction surface of the group of rollers, i.e., the traction surface of the sun roller, the traction surface of the planetary roller, or the surface of the traction track ring, wears the axial load means on the sun roller, then The sun roller exerts a vertical load on the planetary roller due to the conical effect, and the planetary roller automatically adjusts its axial position and radial position and remains pressed between the sun roller and the traction track ring. The traction state necessary for power transmission, that is, the movement of the planetary roller between the sun roller and the traction track ring is maintained. In one aspect of the present invention, the planetary roller may perform the same automatic adjustment operation when the axial load is applied to the traction track ring.

  Preferably, the roller transmission is a line shown below, that is, a longitudinal axis of the roller transmission, a tangent line between the traction surface of the sun roller and the traction surface of each planetary roller, and the mounting shaft. And a tangent line between the traction surface of the planetary roller and the traction trajectory ring has a converging vertex. Depending on how the planetary roller is attached to the planet carrier, the apex is either on the input shaft or on the output shaft.

  In the first embodiment of the present invention, each planetary roller moves on its mounting shaft to adjust its axial position, and its radial position corresponds to the planet in which the mounting shaft of each planetary roller is received and moved. Adjusted by the open radial groove of the carrier. As a result, when the mounting shaft moves in the radial direction on the radial groove, each planetary roller adjusts its position in the same direction.

  In a second preferred embodiment of the present invention, each planetary roller is integrally mounted along its mounting shaft, and the planet carrier is freely fixed in the axial direction and receives one end of each mounting shaft. A rotating base is provided. This allows each planetary roller to adjust its axial position within the planet carrier as the mounting shaft moves within the rotating base. As in the first embodiment, the planet carrier has an open radial groove for adjusting the radial position of the planet roller, and the rotating base is connected to the corresponding open radial groove, respectively. Can move along radial grooves. As a result, when the rotary base moves in the radial direction in the planet carrier, the mounting shaft is in the rotary base, so that each planetary roller also adjusts its radial position.

  In a third preferred embodiment, the axial load means presses the traction track ring, the traction track ring transmits the load as a vertical load to the planetary roller, and the planetary roller has its radial position and axis. The directional position is adjusted between the traction track ring and the sun roller. In the third embodiment, each planetary roller is integrally attached to its mounting shaft, and both end portions of the mounting shaft extend to the bottom surface and the notch surface of the planetary roller, and the planetary roller has both end portions of the mounting shaft. Attached to the planet carrier. The planet carrier includes a rotation base that freely receives both ends of the mounting shaft. The planet carrier is also provided with an open radial groove to allow the rotating base to move in the radial direction, so that the planetary roller can adjust its radial position.

As can be understood from the above, the object of the present invention is a traction self-adjusting planetary roller transmission having a small size but high efficiency and low noise level during operation. It is an object of the present invention to provide an automatic traction planetary roller transmission device that can hold an agent arbitrarily but operates without being used.
The novel aspects believed characteristic of the invention will be established in more detail by the appended claims. However, the invention, together with its objects and advantages, will be better understood when the following detailed description of the preferred embodiment is read with reference to the accompanying drawings, both in terms of construction and manner of operation.

  Referring to the accompanying drawings, and more particularly to FIG. 1, there is shown a longitudinal sectional view of a traction self-adjusting planetary roller transmission 1 constructed in accordance with a first particularly preferred embodiment of the present invention. However, the traction automatic adjustment planetary roller transmission is merely an example, and should not be interpreted in a limited manner. As is apparent from the figure, there is almost no vacant space between the components of the traction automatic adjustment planetary roller transmission 1 so that its structure is extremely compact.

  The traction automatic adjustment planetary roller transmission 1 includes a conical sun roller 10 having a traction surface 11 on a side wall, a traction track ring 20 having a conical surface concentrically spaced from the sun roller 10, and a plurality of cones. And a planetary roller 30. Each planetary roller 30 has a notch surface (a truncated surface) 32, a bottom portion 33, and a traction surface 31 on the side wall portion. In this sense, it can be said that due to the conical shape of the planetary roller, the bottom 33 is defined by the surface having the largest diameter, while the notch surface 32 is the surface facing the bottom 33. The same is true for the surface 10 of the sun roller.

  The planetary roller 30 is disposed in an inclined state between the traction surface 11 of the sun roller 10 and the traction track ring 20. The planetary rollers 30 are also equally spaced around the sun roller 1 so that the traction surface 31 of each planetary roller 30 is in contact with the traction surface 11 of the sun roller 10 and the traction track ring 20. Further, it may be said that each planetary roller 30 includes a mounting shaft 50.

  FIG. 1 further shows a planet carrier 40 on which a planetary roller 30 is rotatably mounted on a notch surface 32 by its mounting shaft 50. As a result, each planet roller 30 can rotate away from the planet carrier 40. Also, each planetary roller 30 adjusts its axial position and radial position between the traction surface 11 of the sun roller 10 and the traction orbit ring 20, so that the planetary carrier 40 can move in the axial direction and the radial direction. It is attached. In the embodiment shown in FIG. 1, the planetary roller adjusts its axial position towards the planet carrier 40. A method for adjusting the axial position and the radial position of each planetary roller in the first embodiment will be described in detail later.

  As another important component shown in FIG. 1, the roller transmission 1 has an input shaft 80 mounted on the sun roller 10 and parallel to the longitudinal axis XX ′ of the roller transmission 1. Yes. Furthermore, an output shaft 85 mounted on the planet carrier 40 and parallel to the input shaft 80 is shown. Finally, the roller transmission shown in FIG. 1 has a housing 90 that protects it. The input shaft 80 is received in the housing 90, and the output shaft 85 protrudes therefrom.

  The traction automatic adjustment planetary roller transmission 1 also includes axial load means such as an elastic washer 70. The elastic washer 70 is arranged so as to surround the input shaft 80 on the housing 90, preferably at the rear part thereof. As part of such an axial load means, a bearing (bearing) 60 that contacts the washer 70 is provided and is mounted on a circumferential sheet portion 14 formed adjacent to the bottom 13 of the sun roller 10. . Similarly, the bearing 60 also contacts the bottom 33 of the planetary roller 30. The washer 70 always presses the bearing 60 to transmit the axial load to the sun roller 10, and at the same time the bearing 60 in contact with the planetary roller 30 is relative to the planetary roller 30, the sun roller 10, and the elastic washer 70. Decrease the angular velocity. Viewed another way, the elastic washer 70 induces a conical effect between the components of the roller transmission to maintain the traction required for its operation, so that power transmission is efficiently maintained.

  As the traction surface 11 of the sun roller 10, the traction surface 31 of the planetary roller 30, or the surface of the traction track ring 20 wears, the washer 70 applies an axial load to the sun roller 10. Then, this time, the sun roller 10 applies a vertical load to the planetary roller 30 by the conical effect to adjust its axial position and radial position, and the planetary roller 30 is again pressed between the sun roller 10 and the traction track ring 20. Kept in a state.

  What should be noted here is that the traction track ring 20 is integrally formed in the housing 90 in the automatic traction planetary roller transmission 1 shown in FIG. This feature reduces the size of the roller transmission. The housing 90 preferably has three parts: (i) a central part 91 having an open front and back and a conical longitudinal section; and (ii) an input shaft 80 for receiving and mounting on the back of the central part 91. And (iii) a front cover 93 attached to the front surface of the central portion 91 from which the output shaft 85 of the housing 90 protrudes.

In the housing 90, the front cover 93 and the back cover 92 are attached to the central portion 91 by bolts, screws, rivets (not shown), or other means for the above purposes. Such means penetrates through corresponding hole portions 95 provided in the central portion 91, the front cover 93, and the back cover 92, respectively.
Preferably, the back cover 92 and the front cover 93 have a cylindrical shape that protrudes from the housing 90, includes a hollow axial extension 94, receives the input shaft 80 in the housing 90, and receives the output shaft 85 in the housing. Derived outside 90.

Referring to FIG. 2 showing a longitudinal section of the upper half of the traction automatic adjustment planetary roller transmission 1, the following is defined in the transmission 1 on the longitudinal axis XX ′ on the output shaft 85 side. It can be seen that there is an intersection A where the lines converge, that is, a “vertex”. These are
(A) A first tangent line B between the traction surface 11 of the sun roller 10 and the traction surface 31 of each planetary roller 30 and forming a first inclination angle α with respect to the longitudinal axis XX ′ of the transmission. ,
(B) the longitudinal axis of the mounting shaft 50 and a line C forming a second inclination angle β with respect to the longitudinal axis XX ′ of the transmission device; and (c) the traction surface 31 and the traction of the planetary roller 30. A second tangent line D that is between the ring 20 and forms a third inclination angle δ with respect to the longitudinal axis XX ′ of the transmission.
It is.

In particular, in order to ensure a pure support state and a minimum reduction in efficiency in the traction automatic adjustment planetary roller transmission 1, the inclination angles described above are related to each other based on the following formula (l).
β = 0.5 (α + δ) (l)
In the pure rolling state, the tangential speed is equal at every contact point between the traction surface 31 of each planetary roller 30 and the traction surface 11 of the sun roller 10, and between the traction surface 31 of each planetary roller 30 and the traction track ring 20. Is also realized when the speeds are equal. In other words, a pure rolling state is understood as a state where there is no slippery area on the traction surface of the transmission 1.

In the first preferred embodiment of the present invention, a very important point is that when the planetary roller 30 is moved in the radial direction and the axial direction, the traction surface of the automatic traction planetary roller transmission device 1 is worn. However, it is thought that it becomes possible to reliably maintain the interrelationship between the angles α, β, and δ given by the vertex A and the equation (l).
In order to describe in detail the other elements of the first preferred embodiment of the present invention, reference is particularly made to FIG. FIG. 3 shows a side view of the sun roller 10 integrally attached to the input shaft 80. Outside the housing, the outer end 81 of the input shaft is connected to a power source (not shown) such as an electric motor. Similarly, as shown in FIG. 3, the sun roller 10 has a traction surface 11, a notch surface 12, and a bottom portion 13, and is provided with a circumferential sheet portion 14 mounted on the bearing 60. The diameter of the circumferential sheet portion is smaller than the diameter of the bottom portion 13 of the sun roller 10.

  FIG. 4 and FIGS. 6 to 8 are all different views showing the planet carrier 40. Among them, in all the drawings other than FIG. 4, the planetary roller 30 is attached to the planet carrier 40. FIG. 4 is a perspective rear view of the planet carrier 40 in which only the mounting shaft 50 is arranged and the planetary roller is not mounted. Of these similar figures, all of the figures other than FIG. 7 show the output shaft 85 attached to the planet carrier 40.

The mounting shaft 50 of each planetary roller 30 is freely received in the planet carrier 40, and each planetary roller 30 can move on the mounting shaft 50 and adjust its axial position in the transmission.
On the other hand, the planet carrier 40 is a disk having an outer surface 41, an inner surface 42, and a side surface 43, and the inner surface 42 is located in front of the planetary roller. The side surface 43 of the planet carrier 40 is provided with an open radial groove 44 that intersects the thickness direction of the planet carrier 40 laterally, and each radial groove 44 is attached to each planetary roller 30. One end of the shaft 50 is received. Each open radial groove allows the mounting shaft 50 to move radially along itself so that each planetary roller can adjust its radial position within the planet carrier 40. become. In some embodiments of the invention, the relationship between the radial length of each open radial groove 44 and the diameter dimension of the mounting shaft 50 is about 1.0 to 1.2.

  Another important aspect of the planet carrier 40 is that a shaft guide 46 corresponding to each open radial groove 44 is provided around the inner side 42 and the open radial groove 44. The guide portions 46 help the mounting shaft 50 maintain the tilted state of the planetary roller 30 in the planetary carrier 40. Preferably, the shaft guide 46 is a hollow projection having a notch-cone-shaped wall and extends upward in a tilted manner from the inner surface 42 of the planet carrier 40 so that the edge of each open radial groove 44 is formed. Covering.

  Referring to FIGS. 4, 5, and 7, each mounting shaft 50 has a head 51 at one end thereof and a vertical connecting portion 52 that is adjacent to the head 51 and has a smaller diameter than the mounting shaft 50. You can see that it has. The head is connected to the outer surface 41 of the planetary carrier 40 and a recess 47 formed around each radial groove 44, and the longitudinal connection 52 extends from the head 51 and extends to each open radial groove 44 and its axial guide. It has a length sufficient to be received within the portion 46. Both the radial groove 44 and its shaft guide 46 have an inner diameter that is smaller than the diameter of the mounting shaft 50 and larger than the diameter of the connecting portion 52. The mounting shaft 50 further includes a radial wall 53 that defines a longitudinal connection 52, and the head 51 and the radial wall 53 hold the mounting shaft 50 in the axial direction within the planet carrier 40. ing. An important feature of the first embodiment is that each mounting shaft 50 moves only in the radial direction, allowing each planetary roller 30 to move in the same direction, while each planetary roller 30 has its axial direction. It is to move along each mounting shaft 50 to adjust the position.

  Now, with particular reference to FIG. 4, an adjustment space, i.e., a vent 45, is provided on the back surface 42 of the planet carrier 40, so that the planet carrier 40 can be connected to the planetary roller during radial and axial position adjustment within the transmission. This prevents contact with the cut-out surface. Preferably, the adjustment space, that is, the vent 45 is a recess whose outer periphery is circular and whose surface is inclined with respect to the inner surface 42, and the depth of the recess is maximized on the side surface 43 of the planetary carrier 40. .

  On the other hand, the planetary carrier 40 is provided with a toothed circumferential recess 49 (see FIGS. 6 and 7) for mounting the output shaft 85 with teeth on the inner end. The attachment of these components is clearly shown in FIG. In order to attach the output shaft 85 to the planet carrier 40, other means, for example, male and female connectors provided on the planet carrier 40 and the inner end of the output shaft 85 may be used.

  The number of planetary rollers 30 varies depending on the requirements of durability and power transmission, but in the planetary roller type transmission device of the present invention, it is particularly preferable to use 3 to 12 planetary rollers. If the number of planetary rollers used is two or less, the durability of the transmission device is drastically reduced. If the number is 13 or more, the space for arranging the rollers and other components of the transmission device becomes a problem. The power transmission relationship becomes unsuitable for almost all industrial applications. More preferably, as shown in FIGS. 1 to 11, which shows the first preferred embodiment of the present invention, the transmission device comprises five planetary rollers, whereby the transmission device of the present invention has a suitable efficiency, It has an excellent output relationship.

  Regarding the manufacturing material of the traction planetary roller type transmission device of the present invention, the sun roller 10, the traction track ring 20, and the planetary roller 30 have a coefficient of static friction exceeding 0.3 and a surface hardness of Shore hardness A-90. Manufactured from metallic materials, polymeric materials, or ceramic materials that meet high specifications. More preferably, the parts of the transmission are made of steel having the traction coefficient and hardness characteristics described above and / or nylon containing glass fiber or rubber filler and / or acetal polymer.

  In another embodiment of the present invention that is not shown in the accompanying drawings, each of the sun roller and the planetary roller includes a core portion and a lining portion that forms a traction surface thereof. In this embodiment, the core portion is manufactured using a metal material, a ceramic material, and / or a polymer material so that the core portion has a high structural rigidity with a dynamic friction coefficient of less than 0.1 and a hardness higher than the traction surface. On the other hand, it is intended to manufacture the lining portion from the materials mentioned in the above embodiment in which the planetary roller and the sun roller are all made of the same material. That is, the lining portion is composed of steel having a coefficient of static friction exceeding 0.3 and a surface hardness exceeding Shore hardness A-90, and / or nylon containing glass fiber or a rubber filling material, and / or an acetal polymer. It is preferable.

  Referring to FIG. 9, there is shown a perspective front view of the planetary roller 30 used in the traction planetary roller transmission of FIG. As described above, each planetary roller 30 has the traction surface 31, the cutout surface 32, and the bottom 33 of the side wall. Similarly, this configuration shows a planetary roller having a longitudinal conduit 34 provided in the center thereof for freely receiving the mounting shaft and an inclined wall 35 connecting the notch surface 32 to the longitudinal conduit 34. ing. The inclined wall portion 35 has the same inclination and dimensions as the outer wall portion of the shaft guide portion 46 shown in FIG. 4, and facilitates the rotation of the planetary roller 30.

  Referring now to FIG. 10, there is shown a bearing 60 that forms part of the axial load means in the transmission device of the first embodiment. As shown in FIG. 10, the bearing 60 is preferably selected from a cylindrical bearing, a ball bearing, and a conical bearing. The bearing used is a cylindrical bearing composed of two covers 61 and 62 and a plurality of cylinders 63 provided therebetween. This type of bearing makes it possible to apply an axial load to the sun roller and at the same time reduce the relative speed between the planetary roller, the sun roller and the elastic washer without hindering its rotational movement.

  Finally, FIG. 11 shows an elastic washer 70 that is also part of the axial load means of the transmission. The elastic washer 70 has a flat bottom portion 71, an upper surface 72 having a smaller diameter than the flat bottom portion 71, and a curved peripheral wall portion 73 extending upward from the flat bottom portion 71 toward the upper surface 72. Although the structure of the axial load means in this embodiment is simple, the feature of the washer 70 allows the bearing 60 to be loaded at all times, and the planets as the transmission traction surfaces 11, 31, and 20 wear. The roller can be adjusted.

  On the other hand, FIG. 12 shows a traction automatic adjustment planetary roller transmission 2 configured according to still another embodiment of the present invention. The embodiment shown in FIG. 12 is similar to the embodiment of FIGS. 1-11 and the same reference numerals are used. However, in the roller transmission 2 of FIG. 12, the output shaft 85 is covered by the shaft housing 86, and a bush (bearing cylinder) 87 is provided between the shaft housing 86 and the output shaft 85. Both the housing and the bushing 87 are disposed within the axial extension 94 of the front cover 93 of the housing 90. With this arrangement, power can be appropriately controlled and processed in the input shaft 85. The other components of the roller transmission device of FIG. 12 are the same as the components described in the roller transmission device of FIG.

Hereinafter, a second preferred embodiment of the present invention shown in FIGS. 13 to 22 will be described. In the second embodiment, the reference numeral to which the prefix “1” is added is used to distinguish the same components as the main components of the first embodiment shown in FIGS. 1 to 11.
FIG. 13 is a longitudinal sectional view of a traction automatic adjustment planetary roller transmission 101 constructed according to a second particularly preferred embodiment of the present invention. As shown in the drawing, the vertex of the roller transmission 101 is on the opposite side of the vertex of the roller transmission 1 of the first embodiment. Nevertheless, it will be appreciated that both embodiments operate on the general principles of the present invention, primarily based on the radial and axial alignment of the planetary roller between the sun roller and the traction track ring.

  More specifically, the traction automatic adjustment planetary roller transmission 101 shown in FIG. 13 includes a conical sun roller 110 having a traction surface on a side wall portion, and a traction having a conical surface concentrically spaced from the sun roller 110. An orbital ring 121 and a plurality of conical planetary rollers 130 are provided. Each planetary roller 130 has a notch surface 132, a bottom portion 133, and a traction surface 131 on a side wall portion, all of which are arranged in an inclined state between the traction surface 111 of the sun roller 110 and the traction track ring 120. Therefore, the traction surface 131 of each planetary roller 130 is in contact with both the traction surface 111 of the sun roller 110 and the traction track ring 121. The planetary rollers 130 are spaced apart from each other at equal intervals around the sun roller 110 and include a mounting shaft 150.

In the second embodiment, each planetary roller 130 is mounted integrally with its mounting shaft 150. Similarly, each planetary roller 130 is rotatably mounted on the bottom surface 133 by its mounting shaft 150, so that each planetary roller 130 rotates away from the planetary carrier 140.
FIG. 13 also shows a planet carrier 140 with a rotating base 148. A mounting shaft 150 of each planetary roller 130 is freely received by each of the rotating bases 148. Since the mounting shaft 150 moves within the rotating base 148, each planetary roller 130 rotates to adjust the axial position within the planet carrier 140. The position adjustment of the planetary roller 130 in the radial direction will be described below.

In the planetary carrier 140, each rotary base 148 cannot move in the axial direction, but can move freely in the radial direction. Therefore, the radial positions of the planetary rollers 130 and the mounting shaft 150 can be adjusted between the traction surface 111 of the sun roller 110 and the traction track ring 120 by the rotation bases 148.
As described above, since the planetary roller 130 is attached to the planetary carrier 140 at the bottom surface 133 thereof, the roller is separated from the planetary carrier 140 when the planetary roller 130 adjusts the axial position in the roller transmission device 101. Let

Further, the traction automatic adjustment planetary roller transmission 101 includes axial load means corresponding to the coil spring 170 in the second embodiment, and the coil spring 170 moves the bottom 113 of the sun roller 110 from the planet carrier 140. Press in the opposite axial direction.
Referring further to FIG. 13, it can be seen that the roller transmission 101 has an input shaft 180 mounted on the sun roller 110 and parallel to the longitudinal axis XX ′ of the planetary roller transmission 101. Also shown is an output shaft 185 mounted on the planet carrier 140 and parallel to the input shaft 180.

  In particular, the coil spring 170 is disposed between the sun roller 110 and the output shaft 185. More specifically, FIG. 13 shows a portion of the coil spring 170 housed in a gap portion 188 included in the inner end of the output shaft 185, and the other portions of the coil spring 170 are separated from the gap portion 188. It protrudes and contacts a recess 115 provided in the sun roller 110 and is supported thereby.

The roller transmission 101 shown in FIG. 13 also has a housing 190 surrounding the roller transmission 101. Input shaft 180 is received by housing 190, from which output shaft 185 projects.
In the roller transmission device 101, the coil spring 170 applies an axial load to the sun roller 110, and the sun roller 110 receiving this presses the planetary roller 130 against the traction track ring 120. Here, it is important to note that the planetary roller 130 can adjust its radial position and axial position between the traction surface 111 of the sun roller 110 and the traction track ring 120. As a result, the traction state required for the operation of the automatic traction planetary roller transmission 110 is maintained as the traction surface 111 of the sun roller 110, the traction surface 131 of the planetary roller 130, and the surface of the traction track ring 120 wear. It becomes possible to do.

  Furthermore, the traction track ring 120 is integrally formed in the housing 190 in order to reduce the size of the roller transmission. The housing 190 in the second embodiment is preferably configured by the following two parts. That is, (i) a conical main body 191 having a longitudinal section with an open front surface, and (ii) a front cover 193 attached to the front surface of the main body 191 from the front cover 193 to the output of the housing 195 A front cover 193 from which the shaft 1185 protrudes.

In the housing 190, the front cover 193 is attached to the main body 191 by means of bolts, screws, rivets, or other similar means, and such means includes both the main body 191 and the front cover 193. It penetrates the corresponding hole 95 provided in the.
The housing 190 preferably has a cylindrical shape and is provided with a pair of hollow axial extensions 194. One of the pair of extension portions introduces the input shaft 180 into the housing 190, and the other axial extension portion leads the output shaft 185 out of the housing 190.

  Similarly, FIG. 13 shows a roller-type transmission device 101 including a first bush 182 disposed between an input shaft 180 and an axial extension 194 into which the input shaft 180 is introduced. The first bush 182 is in parallel with the input shaft and facilitates the rotation of the input shaft 180 when the planetary roller type transmission device 101 operates. Similarly, a second bush 187 is disposed between the output shaft 185 and the axial extension 194 from which the output shaft 185 protrudes. The second bush 184 is in parallel with the output shaft 185 to facilitate its rotation.

Referring to FIG. 14 showing the upper part of the longitudinal section of the traction automatic adjustment planetary roller transmission device 101, the following lines defined in the transmission device 101 converge on the longitudinal axis XX ′ on the input shaft 180 side. It can be seen that there is an intersection A ′, that is, a “vertex”. These are
(A) A first tangent line between the traction surface 111 of the sun roller 110 and the traction surface 131 of each planetary roller 130 and forming a first inclination angle α ′ with respect to the longitudinal axis XX ′ of the transmission. B ',
(B) a longitudinal axis of the mounting shaft 150 and a line C ′ forming a second inclination angle β ′ with respect to the longitudinal axis XX ′ of the transmission device; and (c) a traction surface 131 of the planetary roller 130. And the traction track ring 120, and a second tangent line D ′ forming a third inclination angle δ ′ with respect to the longitudinal axis XX ′ of the transmission.
It is.

Based on the above description of the first embodiment, in order to ensure a pure rolling state and a minimum reduction in efficiency in the traction automatic adjustment planetary roller transmission device 101, the inclination angle described above is expressed by the following formula (lA). It is related on the basis.
β ′ = 0.5 (α ′ + δ ′) (lA)
In the second preferred embodiment of the present invention, it is very important to have a planetary roller 130 that is free to move radially in the planet carrier 140 as the mounting shaft 150 moves axially on the rotating base 148. It is. This is because the relationship between the vertex A ′ and the angles α ′, β ′ and δ ′ given by the equation (1A) is ensured even when the traction surface of the traction automatic adjustment planetary roller transmission 101 is worn. This is because it becomes possible to keep it.

  It is an essential matter in the present invention that the planetary roller can freely adjust its position. For example, in the embodiment of FIG. 1, each planetary roller 30 slides axially within a planetary carrier 40 about a mounting shaft 50 that is radially movable so that the planetary rollers 30 are in the same direction. Moving. On the other hand, in the second preferred embodiment of FIG. 13, each planetary roller 130 moves because its mounting shaft 150 is received by the rotating base 148, and the mounting shaft moves axially in the rotating base 148. Once rotated, it is now possible to move radially within the planet carrier 140.

To further illustrate other components of the second preferred embodiment of the present invention, reference is made to FIG. FIG. 15 is a perspective side plan view of the sun roller 110 attached to the input shaft 180. Outside the housing, the outer end 181 of the input shaft is connected to a power source (not shown) such as an electric motor.
Similarly, FIG. 15 shows the sun roller 110 defined by the notch surface 112 and the bottom surface 113 in addition to the traction surface 111. A concave portion 115 is provided on the surface of the sun roller, and a coil spring 170 is supported therein (see FIG. 13), whereby an axial load can be applied to the sun roller 110. Another important matter of the second embodiment is that the sun roller 110 is integrally attached to the input shaft 180, thereby reducing the number of parts used for assembling the roller transmission. It is having.

On the other hand, FIGS. 16 and 17 are perspective views of the planetary roller 130 from the notch surface 132 side and the bottom surface 133 side, respectively. These drawings show the traction surface 131 as well as the mounting shaft 150 that is integrally attached to the planetary roller 130 to form an integral part. The assembly advantages of the roller transmission, that is, the roller transmission This represents a decrease in the number of parts.
Referring to FIGS. 18, 19, and 20 showing different views of the planet carrier 140, the planetary roller 130 (FIG. 18) having other important elements of the roller transmission 101, for example, the input shaft 180 and the mounting shaft 150, is provided. ), A rotation base 148 (FIGS. 18 and 19), and the like are attached.

  The planet carrier 140 is a disk having an outer surface 141, an inner surface 142, and a side surface 143. In particular, the side surface 143 of the planet carrier 140 is provided with an open radial groove 144 that passes through the planet carrier 140 across the thickness direction. A rotating base 148 is connected to each radial groove 144. As described above, the mounting shaft 150 is received by each rotating base 148 from one of the planetary rollers 130. Each rotating base can move radially over the entire length of these open radial grooves 144 so that the planetary roller 130 adjusts its radial position within the roller transmission.

  Another important feature of the planet carrier 140, particularly shown in FIGS. 19 and 20, is that it has a crowned cutout 149 in the center thereof. The inner end portion of the output shaft 185 is also crowned and connected to the cutout portion. For example, in FIG. 21, the output shaft 185 has a gear 189 at its inner end. Other means for mounting the output shaft 185 to the planet carrier 140 may be used, for example, male and female connectors provided on the planet carrier 140 and the inner end of the output shaft 85. FIG. 21 shows a gap 188 in which a part of the coil spring 170 is received inside and acts as an axial load that presses the sun roller (see FIG. 13).

  Referring to FIG. 22 showing a perspective view of the bush-like rotary base 148 described in the second embodiment, the bush-like rotary base 148 has a front surface 153 in contact with the inner side surface of the planet carrier, and a back surface 152. It has a head 151 that contacts the bottom of the corresponding planetary roller. The diameter of the head 151 is larger than the width dimension of each radial groove of the planet carrier. In this way, axial movement of the rotating base 148 within the planet carrier is prevented.

Here, the important thing to note is to reduce the different angular velocities of each planet roller and planet carrier during operation of the planetary roller transmission. In the second embodiment of the present invention, the reduction of the angular velocity is achieved by the rotating base 148 and, in particular, the bush head 151 that contacts both the planet carrier 140 and the planet roller 130.
Returning to FIG. 22, the bushing 148 shows a longitudinal conduit 154 that receives the mounting shaft 150 and allows axial and rotational movement of the planetary roller 130. Further, the longitudinal conduit 154 may be provided with a bearing to further facilitate the rotational movement of the mounting shaft 150.

  In the description of the second preferred embodiment, the roller transmission has been provided with five planetary rollers, but it is also possible to have three to twelve planetary rollers. If the number of planetary rollers used is two or less, the durability of the transmission device is drastically reduced. If the number of planetary rollers is 13 or more, the space for arranging the rollers and other components of the transmission device becomes a problem. Furthermore, in the latter case, the power transmission relationship is not suitable for almost all industrial applications such as electric equipment (washing machine) and motorcycles.

  In the second embodiment, the sun roller 110, the traction track ring 120, and the rotating base 148 are manufactured from a metal material, a polymer material, or a ceramic material that satisfies the following specifications. That is, the coefficient of static friction exceeds 0.3 for the sun roller 110, the traction track ring 120, and the planetary roller 130, the coefficient of dynamic friction for the rotating base 148 is less than 0.1, and all these components. The hardness needs to exceed the Shore hardness A-90. More preferably, the parts of the roller transmission are preferably made of steel and / or nylon and / or acetal polymer with glass fiber or rubber filling material having the traction coefficient and hardness characteristics described above. .

  In the second embodiment of the present invention, the sun roller 210 and the planetary roller 230 may each be formed of a core portion and a lining portion that forms a traction surface. In the present embodiment, the core portion is made of a metal material, a ceramic material, and / or a polymer material so that the core portion has a high structural rigidity with a dynamic friction coefficient of less than 0.1 and a hardness higher than the traction surface, The lining portion is intended to be manufactured from the materials mentioned in the above embodiment in which the planetary roller 130 and the sun roller 110 are all made of the same material. That is, the lining portion is made of steel and / or nylon containing glass fiber or rubber filling material, and / or acetal polymer, and the material of the lining portion has a coefficient of static friction exceeding 0.3 and a surface hardness of Shore. It is preferable that the hardness is higher than A-90.

  Referring to FIG. 23, there is shown a traction automatic adjustment planetary roller transmission 102 configured according to still another embodiment of the present invention. As shown in the figure, the constituent elements of the third embodiment are basically the same as the constituent elements of the roller transmission shown in FIG. 13, and therefore the same reference numerals are used. However, since the roller transmission device 102 of the third embodiment does not include the rotation base 148 of the roller transmission device of FIG. 13, the number of parts is reduced. However, the roller transmission device 102 of the third embodiment includes the flat washer 160 having the same function as the bearing 60 of the roller transmission device 1 of FIG. 1 in particular, so that the roller of the first embodiment of FIG. It can be seen that it is particularly similar to the electric transmission. More specifically, the flat washer 160 is located on the sun roller 110 and around a shoulder portion integrally formed around the bottom surface 113. In the roller transmission (FIG. 1) of the first embodiment, the function of the flat washer 160 is to reduce the relative angular velocity between the sun roller 110 and the planetary roller 130, thereby preventing frictional resistance. The traction state required for the roller transmission is realized. The other components of the roller transmission of FIG. 23 are the same as the components shown in FIG.

Hereinafter, a third preferred embodiment of the present invention shown in FIGS. 24 to 35 will be described. In the third embodiment, the reference numeral to which the prefix “2” is added is used to distinguish the same components as the main components of the first and second embodiments.
FIG. 24 shows a longitudinal section of the traction automatic adjustment planetary roller transmission 201. Also in the third embodiment, it is important to adjust the radial position and the axial position of the planetary roller 230 between the sun roller 210 and the traction track ring 220. However, in the third embodiment, an axial load is applied to the traction track ring 220. Therefore, due to the conical effect, the traction track ring 220 applies a vertical load to the planetary roller 230, and the traction surface of the roller transmission is worn. Also, the planetary roller 230 remains pressed between the sun roller 210 and the traction track ring 220.

  More specifically, the traction automatic adjustment planetary roller transmission 201 shown in FIG. 24 includes a conical sun roller 210 having a traction surface on a side wall portion, and a traction having a conical surface concentrically spaced from the sun roller 210. An orbital ring 221 and a plurality of conical planetary rollers 230 are provided. Each planetary roller 230 has a notch surface 232, a bottom portion 233, and a traction surface 231 on the side wall portion, all of which are disposed in an inclined state between the traction surface 211 of the sun roller 210 and the traction track ring 220. Therefore, the traction surface 231 of each planetary roller 230 is in contact with both the traction surface 111 of the sun roller 110 and the traction track ring 221. The planetary rollers 230 are spaced apart from each other at equal intervals around the sun roller 210 and include a mounting shaft 250.

  In the third embodiment, each planetary roller 230 has its mounting shaft 250 integrally mounted as a single component. Further, as shown in FIG. 24, both end portions of the mounting shaft 250 extend on the bottom surface 233 and the notch surface 232 of the planetary roller 230, so that each planetary roller 230 is attached to the planet carrier 240 by both end portions of the mounting shaft 250. It rotates away from the planet carrier 240.

  For this assembly, the planetary carrier 240 is provided with a rotating base 248 that freely receives the end of the mounting shaft 250 of the planetary roller 230. As described above, since the mounting shaft 250 can move in the rotation base 248, each planetary roller 230 in the planetary carrier 240 can rotate to adjust its axial position. The radial position adjustment of the planetary roller 230 will be described below.

Within the planetary carrier 240, each rotary base 248 moves freely in the radial direction, and each planetary roller 230 including the mounting shaft 250 has a radial position between the traction surface 211 of the sun roller 210 and the traction trajectory ring 220. Can be adjusted between. A structure peculiar to the planet carrier 240 of the third embodiment will be described later.
Furthermore, the traction automatic adjustment planetary roller transmission 201 of FIG. 24 is provided with an axial load means. The axial load means in the third embodiment is a plurality of coil springs 270 and cams 260 that apply an axial load to the traction track ring 220.

Still referring to FIG. 24, the roller transmission 201 has an input shaft 280 mounted on the sun roller 210 and parallel to the longitudinal axis XX ′ of the roller transmission 1. Also shown is an output shaft 285 attached to the planet carrier 240 and parallel to the input shaft 280.
In FIG. 24, the roller transmission 201 has a housing 290 that protects the roller transmission 201. Input shaft 280 is received in housing 290 from which output shaft 285 protrudes. Unlike the first and second embodiments, in the third embodiment, since the axial load is applied to the traction track ring 220 as described above, the traction track ring 220 is independent of the housing 290.

  In particular, the housing 290 in the third embodiment is composed of the following two parts. That is, (i) a conical main body 291 having a longitudinal section with the back opened, and (ii) a back cover 292 attached to the main body 291. The back cover 292 receives the input shaft 280. In the housing 290, the back cover 292 is attached to the main body 291 by a plurality of screws 296 that pass through corresponding holes 295 provided in the main body 291 and the back cover 292. It is also possible to attach these parts to the housing 290 using rivets, bolts, or similar means.

  As shown in FIG. 24, the housing 290 includes an input bearing 282 that couples with the center of the back cover 292. The input shaft 280 is received in the bearing. Similarly, the output shaft 285 is provided with an output bearing 287. The central portions of the bearings 282 and 287 are arranged in parallel to facilitate rotation of both the input shaft 280 and the output shaft 285 during operation of the planetary roller transmission 201.

Referring to FIG. 25, an upper part of the longitudinal section of the traction automatic adjustment planetary roller transmission 201 is shown. Similar to the above-described embodiment, the intersection A ″, that is, the “vertex” where the following line defined in the roller transmission 201 converges on the vertical axis XX ′ on the input shaft 280 side. I know that there is. These are
(A) A first tangent line between the traction surface 211 of the sun roller 210 and the traction surface 231 of each planetary roller 230 and forming a first inclination angle α ″ with respect to the longitudinal axis XX ′ of the transmission device. B ",
(B) a longitudinal axis of the mounting shaft 250 and a line C ″ forming a second inclination angle β ″ with respect to the longitudinal axis XX ′ of the transmission device; and (c) a traction surface 231 of the planetary roller 230. And the traction track ring 220, and a second tangent line D ″ forming a third inclination angle δ ″ with respect to the longitudinal axis XX of the transmission
It is.

In order to ensure a pure support state and a minimum reduction in efficiency in the traction automatic adjustment planetary roller transmission 201, the inclination angles described above are related to each other based on the following formula (1B).
β ″ = 0.5 (α ″ + δ ″) (1B)
In a third preferred embodiment of the present invention, the mounting shaft 250 includes a planetary roller 230 that can move axially on the rotating base 248 and move freely in the radial direction within the planetary carrier 240. Thus, even when the traction surface of the traction automatic adjustment planetary roller transmission 201 is worn, the vertex A ″ is reliably maintained, and the interrelationship between the angles α ″, β ″ and δ ″ given by the equation (1B) is obtained. It becomes possible to keep reliably. The vertices can also be found on the output shaft 285, depending on the way the planetary roller 230 is mounted in the planet carrier 240.

  To further illustrate other components of the third preferred embodiment of the present invention, reference is made specifically to FIG. FIG. 26 is a perspective side view of the sun roller 210 integrally attached to the input shaft 280. Outside the housing, the outer end 281 of the input shaft is connected to a power source (not shown) such as an electric motor or an internal combustion engine. Similarly, FIG. 26 shows a sun roller 210 defined by a cut-out surface 212 and a bottom surface 213 in addition to the traction surface 211. In this embodiment, the sun roller 210 is integrally attached to the input shaft 280. As clearly shown in FIG. 24, the bottom surface 213 of the sun roller 210 is provided with a shoulder 214 that contacts the bottom surface 233 of the planetary roller 230. The shoulder 214 reduces the angular velocity between the planetary roller 230 and the planet carrier 240 when the roller transmission 201 is operated (see FIG. 24).

  On the other hand, FIG. 27 is a side view of the planetary roller 230, in which a notch surface 232 and a bottom surface 233 are shown. The drawing shows a traction surface 231 and a mounting shaft 250 that is integrally mounted on the planetary roller 230. Further, both ends of the mounting shaft extend beyond the notch surface 232 and the bottom surface 233, whereby the planetary roller 230 is attached to the planet carrier at both ends of the mounting shaft 250 as will be described below.

  28 to 32, the planet carrier 240 according to the third embodiment includes an outer surface 241A, an inner surface 242A, a side surface 243A, and an open radial groove 244A (FIG. 29) formed on the inner surface 242A. And a first disk 240A having an outer surface 241B, an inner surface 242B, a side surface 243B, and an open radial groove 244B (see FIGS. 31 and 32) formed on the inner surface. It can be said that the second disk 240B is integrated. As shown in FIG. 28, between the second disk 240B and the first disk 240A, the planetary roller 230 is placed between the inner surface 241A of the first disk 240A and the inner surface of the second disk 240B. A sufficient distance is provided between 241B and 241B.

  As a part of the planet carrier 240, there are provided a plurality of support portions 238 that are arranged in the lateral direction between the first disk 240A and the second disk 240B and are attached to both disks. Accordingly, each support portion 238 is disposed between one and the other planetary rollers 230 to form a cage-like planetary carrier 240. Finally, as described above, the planet carrier 240 is provided with a rotating base 248 that freely connects both ends of the mounting shaft 250 of each planet roller 230, whereby each planet roller 230 is axially disposed within the planet carrier. The position can be adjusted. In the third embodiment described above, the rotating base 248 is a bearing having a dynamic friction coefficient of less than 0.1, but other similar devices having such a traction coefficient may be used.

  For each planetary roller 230, a rotating base 248 connected to one end of the mounting shaft 250 is received in the radial groove 244A of the first disk 240A and connected to the other end of the mounting shaft 250. 248 is received in the radial groove 244B of the second disk 240B so that the rotational base 248 of each planetary roller 230 is along the radial grooves 244A, 244B of the first and second disks 240A, 240B, respectively. As a result, the radial position of the planetary roller 230 is adjusted.

  Each of the radial grooves 244A of the first disk 240A has a rectangular tear or cut portion having an inclined surface such as a ramp (ramp) that increases in depth toward the center of the first disk 243A (FIG. 29). And FIG. 30). On the other hand, the radial groove 244B of the second disk 240B is also formed as a rectangular tear or cut-out part (FIGS. 31 and 32) having an inclined surface, and the depth thereof is the same as that of the second disk 240B. It increases as it approaches the side surface 243B. In other words, the depth of the radial groove 244B of the second disk 240B varies in the opposite direction to that of the first disk 240A, thereby allowing the planetary roller to be correctly adjusted in the radial direction. Is brought about. Further, FIG. 32 shows a central opening 249 that receives a sun roller that contacts the planetary roller.

  31 and 32, a support portion 238 integrally attached to the second disk 240B including the hole portion 239B corresponding to the hole portion 239A of the first disk 240A (FIGS. 29 and 30) is shown. Yes. The holes receive screws or other similar means to attach the first disk 240A to the support 238, thereby forming the cage structure of the planet carrier 240.

The first disk 240A of the planet carrier 240 is preferably attached integrally to the output shaft 285. However, these components may be joined by gears, male and female connectors, or the like.
Hereinafter, FIGS. 33 to 35 will be referred to in order to explain the structure of the axial load means. Each of the axial load means includes a plurality of coil springs 270 that are supported at one end and contact the inside of the housing, particularly the back cover 292. The other end of each coil spring 270 is received inside the wall of the traction track ring 220, particularly in the hole 221, and presses it axially. The above structure is also shown in FIG. An axial load cam 260 provided as the other member of the axial load means of the third embodiment is provided on the housing, preferably the back cover 292, and includes an offset portion 261 having an inclined side wall. Each offset 261 is received by another member that cooperates geometrically, such as an ear 262 having an inclined sidewall provided at the rear of the traction track ring 220.

  The axial load means operates as follows. Upon receiving the minimum power required by the roller transmission, the spring 270 applies an axial preload to the traction track ring 220 and, depending on the torsional couple required by the roller transmission, the track ring 220. Rotates slightly in response to the minimum power required. Then, the inclined side wall of the offset portion 261 contacts and slides on the inclined wall of the other member, that is, the ear portion 262 exhibits a wedge effect, thereby causing the traction track ring 220 to move in the axial direction. Press. Under the axial load from the spring 270 and cam 260, the conical effect causes the orbital ring 220 to apply a vertical load to the planetary and sun rollers, resulting in the traction required for power transmission. The structure of the axial load means is extremely useful for such a transmission device used in a motorcycle.

In an embodiment not shown, the other member that geometrically cooperates with the offset portion 261 may be provided in the traction track ring as a slit or cooperating recess that contacts the offset portion 261.
The axial load applied to the traction track ring can also be realized by other methods as shown in FIG. FIG. 36 is a schematic view of the planetary transmission device 201, and the planet carrier is not shown. However, it should be understood that the planetary roller 230 is mounted on the aforementioned planet carrier 240 together with its mounting shaft 250. Similarly, for the sake of explanation, the input shaft 280 and the output shaft 285 are maintained. In FIG. 36, the axial load is applied to the traction track ring 220 by an axial load cam indicated by reference numeral 260A. The axial load cam 260A is supported by the housing 290 and surrounds the input shaft 280, the second annular portion 262A attached to the traction track ring 220, and the first and second annular portions. It is formed by a plurality of movable cylindrical rollers 263 disposed between the portions 261A and 262A. The traction track ring 220 rotates slightly on the first annular portion 262A supported by the cylindrical roller 263 together with the second annular portion 262A according to the twist couple required in the roller transmission. As a result, the track ring 220 can be pressed in the axial direction, and a traction state required for power transmission is realized.

From another point of view, the necessary vertical load is applied to the planetary roller and the sun roller when an axial load is applied to the traction track ring due to the conical structure of the roller transmission, that is, the presence of the “vertex”. As a result, angular velocity and tangential force are transmitted.
In the third embodiment described above, the roller transmission device includes four planetary rollers. However, it can also include three to twelve planetary rollers. The number of planetary rollers depends on the aforementioned factors. In the third embodiment, both the traction track ring 220 and the planetary roller 230 are manufactured from a metal material, a polymer material, or a ceramic material that satisfies the following specifications. That is, the static friction coefficient is greater than 0.3 for the sun roller 210, the traction track ring 220, and the planetary roller 230, and the dynamic friction coefficient is less than 0.1 for the rotating base 248, while all these components The hardness needs to exceed the Shore hardness A-90. More preferably, the parts of the roller transmission are preferably made of steel and / or nylon containing glass fiber or rubber filler material and / or acetal polymer having the traction coefficient and hardness characteristics described above.

  In the third embodiment of the present invention, each of the sun roller 210 and the planetary roller 230 may be formed of a core portion and a lining portion that forms a traction surface thereof. In the present embodiment, the core portion is made of a metal material, a ceramic material, and / or a polymer material so that the core portion has a high structural rigidity with a dynamic friction coefficient of less than 0.1 and a hardness higher than the traction surface, The lining portion is intended to be manufactured using the materials mentioned in the above embodiment in which the planetary roller 230 and the sun roller 210 are all made of the same material. That is, the lining portion is made of steel and / or nylon containing glass fiber or rubber filling material, and / or acetal polymer, and the material of the lining portion has a coefficient of static friction exceeding 0.3 and a surface hardness of Shore. It is preferable that the hardness is higher than A-90.

In general, one of the important features of the traction self-adjusting planetary roller transmission of the present invention is that it operates without the use of costly traction or elastohydrodynamic lubricants. However, the roller transmission may include any one of the lubricants in the housing to realize an appropriate operation.
As described above, the roller transmission of the present invention includes the planetary roller that automatically adjusts the position as the roller transmission traction surface wears even when the apex is on the input shaft side or the output shaft side. Thus, the traction state necessary for the operation can be maintained. Similarly, according to the present invention, it is possible to bring the traction surfaces of all the rollers into contact with each other by the axial load, thereby realizing a traction state necessary for power transmission. The axial load may be realized by elastic washers and bearings, coil springs, cams, or other similar means that press only the sun roller. Furthermore, an axial load may be applied to the raceway ring using the aforementioned load cam. In other words, the purpose of the axial load means is to bring the traction surfaces of the roller transmission into contact with each other. If the planetary roller cannot move in the axial direction and the radial direction, the contact state between such traction surfaces Can not be maintained for a long time.

  Yet another advantage of the roller transmission of the present invention is that the structure is extremely compact because there is little free space between the components. Also, its operation is extremely quiet at less than 60 dB (dB), the mechanical efficiency is at least 96%, and it operates without vibrations thanks to its structure and the material choices that make up the traction surface. Therefore, the traction self-adjusting planetary roller transmission is suitable for a washing machine, a motorcycle, or any other device that needs to change the power supplied from a power source having a specific relationship.

  While the present invention has been described with reference to particular embodiments, it should be noted that, for example, the number of planetary rollers, manufacturing materials, and the use of elastohydrodynamic lubricants without departing from the scope of the true invention. It is possible to improve the above embodiments, such as the length of the radial groove, the method of receiving the shaft in the housing, and the like. Accordingly, the invention is not limited except as described in the state of the art and the appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view of a traction automatic adjustment planetary roller transmission configured according to a first preferred embodiment of the present invention. It is a figure which shows the upper half part of the traction automatic adjustment planetary roller type transmission device of FIG. 1, Comprising: The vertex which the specific line defined in this roller type transmission device converges is shown. FIG. 2 is a perspective side view of a sun roller attached to an input shaft, which is a part of the automatic traction planetary roller transmission device of FIG. 1. FIG. 2 is a perspective rear view of a planet carrier that is a component of a part of the traction automatic adjustment planetary roller transmission shown in FIG. 1 and shows the configuration of its mounting shaft. It is a longitudinal cross-sectional view of one attachment shaft used for the traction automatic adjustment planetary roller type transmission device of FIG. FIG. 2 is a perspective front view of a planet carrier to which a planetary roller is attached, which is a part of the traction automatic adjustment planetary roller transmission shown in FIG. 1. FIG. 7 is a front plan view of the planet carrier and the planet roller shown in FIG. 6. FIG. 7 is a perspective rear view of the planet carrier and planet roller shown in FIG. 6. FIG. 2 is a perspective front view of a planetary roller used in the traction automatic adjustment planetary roller transmission device shown in FIG. 1. FIG. 2 is a perspective plan view of a bearing, which is a part of an axial load means used in the traction automatic adjustment planetary roller transmission of FIG. 1. FIG. 2 is a side plan view of an elastic washer that is a part of an axial load means used in the traction automatic adjustment planetary roller transmission device of FIG. It is a longitudinal cross-sectional view of the traction automatic adjustment planetary roller type transmission device comprised by other embodiment of this invention. It is a longitudinal cross-sectional view of the traction automatic adjustment planetary roller type transmission apparatus comprised by the 2nd preferable embodiment of this invention. FIG. 14 is a diagram showing an upper half portion of the traction automatic adjustment planetary roller transmission device of FIG. 13, showing a vertex at which a specific line defined in the roller transmission device converges. It is a perspective plane side view of the sun roller attached to the input shaft which is a part of the traction automatic adjustment planetary roller transmission device shown in FIG. FIG. 14 is a perspective side plan view of a planetary roller used in the traction automatic adjustment planetary roller transmission device of FIG. 13 and its mounting shaft. FIG. 14 is a perspective side plan view of a planetary roller used in the traction automatic adjustment planetary roller transmission device of FIG. 13 and its mounting shaft. FIG. 14 is a perspective front view of a planet carrier that is a component of a part of the traction automatic adjustment planetary roller transmission of FIG. 13, in which the planetary roller is attached to a rotating base. FIG. 19 is a perspective front view of the planetary carrier shown in FIG. 18 including only a rotating base. FIG. 19 is a perspective front view of the planet carrier shown in FIG. 18 without any components attached. FIG. 14 is a perspective side plan view of an output shaft of the traction automatic adjustment planetary roller transmission device of FIG. 13. It is a perspective side top view of a rotation base. It is a longitudinal cross-sectional view of the traction automatic adjustment planetary-roller type transmission apparatus comprised by other embodiment of this invention. It is a perspective longitudinal cross-sectional view of the traction automatic adjustment planetary roller type transmission device comprised by the 3rd preferable embodiment of this invention. It is a figure which shows the upper half part of the traction automatic adjustment planetary roller type transmission device of FIG. 24, Comprising: The vertex which the specific line defined in this roller type transmission device converges is shown. It is a perspective plane side view of the sun roller attached to the input shaft which is a part of the traction automatic adjustment planetary roller type transmission device of FIG. FIG. 25 is a side view of a planetary roller used in the planetary roller type transmission device of FIG. 24 and its mounting shaft. It is a perspective front view of the planet carrier which is a part of component of the traction automatic adjustment planetary roller type transmission device of FIG. 24, and the planetary roller is attached to the rotation base. FIG. 25 is a perspective plan view of a first disk that is a part of a planet carrier used in the planetary roller transmission of FIG. 24. FIG. 25 is a perspective plan view of a first disk that is a part of a planet carrier used in the planetary roller transmission of FIG. 24. FIG. 25 is a perspective plan view of a second disk that is a part of the planet carrier used in the planetary roller transmission of FIG. 24. FIG. 25 is a perspective plan view of a second disk that is a part of the planet carrier used in the planetary roller transmission of FIG. 24. FIG. 25 is a perspective side view of a housing rear cover and a traction track ring used in the planetary roller transmission of FIG. 24. FIG. 34 is a perspective front view of the housing rear cover of FIG. 33. FIG. 34 is a perspective rear view of the traction track ring shown in FIG. 33. It is a side view of the axial direction load means which can be integrated in the planetary roller type transmission device of FIG.

Claims (51)

A traction automatic adjustment planetary roller transmission,
(A) a conical sun roller having a bottom, a cut-out surface, and a traction surface of a side wall;
(B) a traction track ring having a conical surface and concentrically spaced from the sun roller;
(C) A plurality of conical planetary rollers each having a bottom, a cut-out surface, and a traction surface on a side wall, all of which are inclined between the traction surface of the sun roller and the traction track ring. A conical planetary roller including a mounting shaft, the traction surface of each planetary roller being in contact with the traction surface of the sun roller and the traction track ring, spaced apart from each other around the sun roller; ,
(D) a planet carrier, wherein each planet roller is rotatably mounted by its mounting shaft, each planet roller rotates away from the planet carrier, and each planet roller has its radial position and axial direction A planet carrier mounted for axial and radial movement within the planet carrier so that its position can be adjusted between the traction surface of the sun roller and the traction orbit ring;
(E) an input shaft mounted on the sun roller and parallel to the vertical axis of the roller transmission,
(F) an output shaft mounted on the planet carrier and parallel to the input shaft;
(G) an axial load means for pressing the bottom of the sun roller;
(H) a housing that covers the roller transmission, the housing receiving the input shaft, and the output shaft protruding therefrom;
As the traction surface of the sun roller, the traction surface of the planetary roller, or the surface of the traction track ring wears, the axial load means applies a load to the sun roller, and then the sun roller causes the planetary effect by a conical effect. A vertical load is applied to the roller, whereby the planetary roller adjusts its axial position and radial position to remain pressed between the sun roller and the traction track ring, and the traction state necessary for power transmission A traction automatic adjustment planetary roller transmission characterized in that   The traction automatic adjustment planetary roller transmission according to claim 1, wherein the traction track ring is integrally formed in the housing. The transmission is located between the following lines, that is, between the traction surface of the sun roller and the traction surface of each planetary roller, and forms a first inclination angle α with respect to the longitudinal axis of the roller transmission. 1 tangent,
A line that forms a second inclination angle β with respect to the longitudinal axis of the mounting shaft, with respect to the longitudinal axis of the roller transmission,
A vertex between the planetary roller traction surface and the traction trajectory ring that converges with a second tangent line forming a third inclination angle δ with respect to the longitudinal axis of the roller transmission is on the longitudinal axis. Have
In order to ensure a pure rolling state and a minimum reduction in efficiency in the roller transmission, the inclination angle is expressed by the following formula (l)
β = 0.5 (α + δ) (l)
The traction automatic adjustment planetary roller transmission according to claim 1, wherein the traction automatic adjustment planetary roller transmissions are related to each other.   4. The traction automatic adjustment planetary roller transmission according to claim 3, wherein the apex is located on the output shaft.   4. The traction automatic adjustment planetary roller transmission according to claim 3, wherein the apex is located on the input shaft.   The mounting shaft of each planetary roller is freely received therein, whereby each planetary roller moves on the mounting shaft and adjusts its axial position, and the planetary carrier has an outer surface, an inner surface, and a side. A disk having an open radial groove extending from one side to the other across the width direction of the planet carrier, each of the radial grooves being one piece. The end of the mounting shaft of the planetary roller is received, thereby allowing the mounting shaft to move radially along the radial groove so that each planetary roller is in its radial position. The traction automatic adjustment planetary roller transmission according to claim 1, wherein the traction is adjusted in the planet carrier.   The planetary carrier has a shaft guide associated with each open radial groove on its inner surface, the shaft guides each assisting the mounting shaft to keep the planetary roller tilted within the planetary carrier. The guide portion is a hollow projection portion having a notch-conical wall portion, and extends upward in an inclined state beyond the edge of each open radial groove from the inner surface of the planet carrier. The traction automatic adjustment planetary roller transmission device according to claim 6, wherein the traction automatic adjustment planetary roller transmission device is extended.   The mounting shaft of the planetary roller has, at one end thereof, a head, a diameter smaller than that of the mounting shaft, a vertical connecting portion adjacent to the head, and a radial wall defining the vertical connecting portion. The head is coupled to the outer surface of the planet carrier and a recess formed around the edge of each radial groove, the coupling portion being each open radial groove and each shaft guide. The radial groove and each shaft guide portion have an inner diameter that is smaller than the diameter of the mounting shaft and greater than the diameter of the connecting portion. 8. The traction self-adjusting planetary roller transmission according to claim 7, wherein the head and the radial wall portion fix and hold the mounting shaft in the axial direction in the planet carrier. apparatus.   Each planetary roller has a longitudinal conduit for receiving the mounting shaft in the center thereof, and an inclined wall for connecting a notch surface to the longitudinal conduit, the inclined wall being attached to the planet carrier. The traction automatic adjustment planetary roller transmission according to claim 7, wherein the traction automatic adjustment planetary roller transmission device has the same inclination and dimensions as the outer wall portion of each shaft guide portion provided.   The planetary carrier has an adjustment space on its inner surface that prevents the planetary carrier from coming into contact with the cutout surface of the planetary roller when the planetary roller adjusts its radial position and axial position. The traction automatic adjustment planetary roller transmission according to claim 6.   The adjustment space is formed as a plurality of recesses, and the recesses have a circular outer periphery and a surface inclined with respect to the inner surface of the planet carrier, and the depth thereof is the side surface of the planet carrier. The traction automatic adjustment planetary roller transmission device according to claim 10, wherein the traction automatic adjustment planetary roller transmission device is provided.   Each planetary roller is integrally mounted on its mounting shaft to form one member, and the planetary carrier has a disk having an outer surface, an inner surface, and a side surface, A rotating base that has an open radial groove that crosses the width direction and extends from one side to the other on its side surface, is fixed in the axial direction, and freely receives the end of each mounting shaft inside. Whereby each planetary roller can adjust its axial position within the planet carrier when the mounting shaft moves within the rotating base, and each rotating base is in a radial groove. 2. A traction self-adjusting planetary roller system according to claim 1, characterized in that it is connected and can move radially along the radial groove so that the planetary roller adjusts its radial position. Transmission device.   Each rotating base is a bush having a front surface in contact with the inner surface of the planet carrier and a back surface in contact with the corresponding bottom of the planetary roller, the head having a diameter of each radial groove. The traction automatic according to claim 12, characterized in that it is larger than the width dimension and fixed in the axial direction, the bushing also having a longitudinal conduit for receiving the mounting shaft of the planetary roller. Adjusting planetary roller transmission.   14. The automatic traction planetary roller transmission according to claim 13, wherein a bearing is included in the conduit to facilitate rotation of the mounting shaft of the planetary roller.   Each rotary base is manufactured from a material selected from the group consisting of a metal material, a polymer material, and a ceramic material, and the material has a dynamic friction coefficient of less than 0.1 and a surface hardness of more than Shore hardness A-90. The traction automatic adjustment planetary roller transmission according to claim 13, wherein the transmission is high.   Each rotating base is manufactured from a material selected from the group consisting of steel, nylon having glass fiber or rubber filling material, and acetal polymer having the traction coefficient and the surface hardness. The traction automatic adjustment planetary roller transmission according to claim 15.   The axial load means is supported by the housing and is mounted on an elastic washer that surrounds the input shaft, and a circumferential sheet portion formed in contact with the washer and adjacent to the bottom of the sun roller. The bearing further contacts the planetary roller, whereby the washer constantly presses the bearing to transmit the axial load to the sun roller, and at the same time the bearing is in contact with the planetary roller. 2. The traction automatic adjustment planetary roller transmission according to claim 1, wherein a relative angular velocity among the planetary roller, the sun roller, and the elastic washer is decreased at the time of contact.   The traction self-adjusting planetary roller transmission according to claim 17, wherein the bearing is selected from the group consisting of a cylindrical bearing, a ball bearing, and a conical bearing.   The traction automatic adjustment planetary roller transmission device according to claim 1, wherein the axial load means is a coil spring located between the output shaft and the bottom of the sun roller.   A part of the coil spring is accommodated in the gap formed at the inner end of the output shaft, and the other part of the coil spring protrudes from the gap and is provided at the bottom of the sun roller. The traction self-adjusting planetary roller transmission according to claim 19, wherein the traction automatic adjustment planetary roller transmission is in contact with and supported by the recessed portion.   The axial load means further includes a flat washer, and the flat washer is disposed on the sun roller and around a shoulder formed integrally around the bottom surface of the sun roller, The traction self-adjusting planetary roller transmission according to claim 19, wherein the relative angular velocity with the sun roller is decreased.   The traction automatic adjustment planetary roller transmission according to claim 1, wherein the sun roller is integrally mounted on the input shaft to form one member.   The traction automatic adjustment planetary roller transmission device according to claim 1, comprising three to twelve planetary rollers.   The housing includes a pair of hollow axial extensions having a cylindrical shape, one of the extensions receiving and introducing the input shaft into the housing, and the other axial extension is The traction automatic adjustment planetary roller transmission according to claim 1, wherein the output shaft is led out toward the outside of the housing.   A first bushing disposed between the input shaft and the axial extension that receives the input shaft, the first bushing facilitating rotation and centering of the input shaft; The traction automatic adjustment planetary roller transmission according to claim 24.   A second bushing is further disposed between the output shaft and the axial extension on which the output shaft protrudes, and the second bushing facilitates rotation and centering of the output shaft. The traction automatic adjustment planetary roller transmission according to claim 24.   The sun roller, the traction track ring, and the planetary roller are all manufactured from a material selected from the group consisting of a metal material, a polymer material, and a ceramic material, and the material has a coefficient of static friction exceeding 0.3, 2. The traction automatic adjustment planetary roller transmission according to claim 1, wherein the surface hardness is higher than the Shore hardness A-90.   The sun roller, the traction track ring, and the planetary roller are materials selected from the group consisting of steel, nylon containing glass fiber or rubber filling material, and acetal polymer having the traction coefficient and the surface hardness. The traction automatic adjustment planetary roller transmission according to claim 27, wherein the traction automatic adjustment planetary roller transmission is manufactured by:   2. The automatic traction planetary roller transmission device according to claim 1, wherein the sun roller and the planetary roller include a core portion and a lining portion that forms a traction surface.   The core part is manufactured from a material selected from the group consisting of a metal material, a ceramic material, and a polymer material. The material of the core part has a dynamic friction coefficient of less than 0.1 and a surface hardness of Shore hardness A-90. On the other hand, the lining part is manufactured from a material selected from the group consisting of steel, nylon containing glass fiber or rubber filling material, and acetal polymer, and all the materials of the lining part have a coefficient of static friction. 30. The traction automatic adjustment planetary roller transmission according to claim 29, wherein the traction automatic adjustment planetary roller transmission is greater than 0.3 and has a surface hardness higher than Shore hardness A-90.   2. The traction automatic adjustment planetary roller transmission according to claim 1, wherein an elastohydrodynamic lubricant is optionally contained in the transmission housing. A traction automatic adjustment planetary roller transmission,
(A) a conical sun roller having a bottom, a cut-out surface, and a traction surface of a side wall;
(B) a traction track ring having a conical surface concentrically spaced from the sun roller;
(C) A plurality of conical planetary rollers each having a bottom, a cut-out surface, and a traction surface on a side wall, all of which are inclined between the traction surface of the sun roller and the traction track ring. The planetary roller traction surface is in contact with the traction surface of the sun roller and the traction track ring, and is spaced apart from each other at equal intervals around the sun roller, and includes a conical planetary roller including a mounting shaft. When,
(D) a planetary carrier, wherein each planetary roller is rotatably mounted by its mounting shaft, each planetary roller is rotated away from the planetary carrier, and each planetary roller is axially and within the planetary carrier. A planetary carrier mounted movably in the radial direction and for each planetary roller adjusting its radial position and axial position between the traction surface of the sun roller and the traction orbit ring;
(E) an input shaft mounted on the sun roller and parallel to the vertical axis of the roller transmission,
(F) an output shaft mounted on the planet carrier and parallel to the input shaft;
(G) an axial load means for pressing the traction track ring;
(H) a housing that covers the roller transmission and receives the input shaft, wherein the output shaft protrudes from the housing;
As the traction surface of the sun roller, the traction surface of the planetary roller, or the surface of the traction track ring wears, the axial load means applies a load to the traction track ring, and then the traction track ring is caused by a conical effect. A vertical load is applied to the planetary roller, whereby the planetary roller adjusts its axial position and radial position and remains pressed between the sun roller and the traction track ring, which is necessary for power transmission. A traction automatic adjustment planetary roller transmission characterized by maintaining a traction state. The transmission is located between the following lines, that is, between the traction surface of the sun roller and the traction surface of each planetary roller, and forms a first inclination angle α ″ with respect to the longitudinal axis of the roller transmission. A first tangent line;
A line that forms a second inclination angle β ″ with respect to the longitudinal axis of the mounting shaft with respect to the longitudinal axis of the roller transmission,
A vertex between the planetary roller traction surface and the traction trajectory ring that converges with a second tangent line that forms a third inclination angle δ ″ with respect to the longitudinal axis of the roller transmission is the longitudinal axis. Have on,
In order to ensure a pure rolling state and a minimum reduction in efficiency in the roller transmission, the inclination angle is expressed by the following formula (1B).
β ″ = 0.5 (α ″ + δ ″) (lB)
33. A traction self-adjusting planetary roller transmission according to claim 32, characterized in that they are interrelated with each other.   34. The traction automatic adjustment planetary roller transmission according to claim 33, wherein the apex is located on the output shaft.   The traction automatic adjustment planetary roller transmission according to claim 33, wherein the vertex is located on the input shaft. Each planetary roller is integrally mounted on its mounting shaft to form one member, and both end portions of the mounting shaft extend on the bottom surface and the notch surface of the planetary roller,
A first disk having an outer surface, an inner surface formed with an open radial groove, and a side surface;
A second disk having an outer surface, an inner surface formed with an open radial groove, and a side surface, wherein the inner surface of the first disk and the inner surface of the second disk A second disk spaced from the first disk by a distance sufficient to mount the plurality of planetary rollers therebetween,
The planetary carrier is disposed in a transverse direction between the first disk and the second disk and is attached to the first disk and the second disk, each positioned between the planetary rollers. A plurality of support portions giving a cage shape to
A rotating base that is freely connected to both ends of the mounting shaft of each planetary roller;
As a result, each planetary roller can adjust its axial position within the planet carrier, and the rotating base connected to one end of the mounting shaft of each planetary roller is the first disk. The other rotating base connected to the radial groove and connected to the other end of the mounting shaft is connected to the radial groove of the second disk, whereby both rotating bases of the planetary roller are connected. 33. The platform of claim 32, wherein a platform is movable over the radial grooves of each of the first and second disks, so that the radial roller position is adjusted. Traction automatic adjustment planetary roller transmission.   37. Each of the radial grooves of the first disk is formed as a rectangular cutout having an inclined bottom, and the depth thereof increases as it approaches the center of the first disk. Traction automatic adjustment planetary roller type transmission device described in 1.   Each radial groove of the second disk is formed as a rectangular cutout with an inclined bottom, and the depth increases as the depth approaches the side surface of the second disk. The traction automatic adjustment planetary roller transmission according to claim 36.   The traction automatic adjustment planetary roller transmission according to claim 36, wherein the both rotation bases are bearings.   The traction automatic adjustment planetary roller transmission according to claim 36, wherein the first disk of the planet carrier is integrally attached to the output shaft to form one member.   The traction automatic adjustment planetary roller transmission according to claim 36, wherein the support portion is integrally attached to the second disk to form one member. The axial load means includes a plurality of coil springs that have one end in contact with the inner portion of the housing and the other end received in the wall portion of the traction track ring to press the traction track ring in the axial direction. ,
An axial load cam formed in the housing and having a plurality of offset portions having inclined side walls, each offset portion being provided on a rear wall portion of the traction track ring, and geometrically cooperating An axial load cam received by the corresponding member
When receiving the minimum power required by the roller transmission, the spring applies an axial preload to the traction track ring, depending on the torsional couple required by the roller transmission. The track ring rotates slightly in response to the minimum required power, and the inclined sidewall of the offset portion contacts the geometrically cooperating corresponding member to axially move the traction track ring On the other hand, upon receiving the axial load from the spring and the cam, the orbital ring transmits the axial load as a vertical load to the planetary roller and the sun roller. The traction automatic adjustment planetary roller transmission according to claim 32, wherein a traction state required for transmission is realized.   The geometrically cooperating corresponding member is provided on the rear wall portion of the traction track ring, and is an ear portion having an inclined wall or a slit having an inclined wall. Automatic traction planetary roller transmission. The axial load means is a load cam,
A first annular portion supported by the housing around the input shaft, and a second annular portion attached to the traction track ring;
A plurality of movable cylindrical rollers disposed between the first and second annular portions, and a load cam comprising:
Thereby, depending on the torsional couple required by the roller transmission, the traction track ring and the second annular part rotate slightly in the first annular part supported on the cylinder. 33. The traction automatic adjustment planetary roller transmission according to claim 32, wherein the traction track ring is moved in the axial direction to realize a traction state required for power transmission.   33. The traction automatic adjustment planetary roller transmission according to claim 32, wherein the sun roller is integrally mounted on the input shaft to form one member.   The traction automatic adjustment planetary roller transmission device according to claim 32, comprising three to twelve planetary rollers.   The sun roller, the traction track ring, and the planetary roller are all manufactured from a material selected from the group consisting of metal materials, polymer materials, and ceramic materials, all of which have a coefficient of static friction of 0.3. The traction automatic adjustment planetary roller transmission according to claim 32, wherein the traction self-adjusting planetary roller transmission device has a surface hardness exceeding the Shore hardness A-90.   The sun roller, the traction track ring, and the planetary roller are made of a material selected from the group consisting of steel, nylon containing glass fiber or rubber filling material, and acetal polymer having the traction coefficient and the surface hardness. The traction automatic adjustment planetary roller transmission according to claim 47, wherein the traction automatic adjustment planetary roller transmission is manufactured.   The traction automatic adjustment planetary roller transmission device according to claim 32, wherein the sun roller and the planetary roller include a core portion and a lining portion that forms a traction surface.   The core part is manufactured from a material selected from the group consisting of a metal material, a ceramic material, and a polymer material. On the other hand, the lining part is manufactured from a material selected from the group consisting of steel, nylon containing glass fiber or rubber filling material, and acetal polymer, and the material of the lining part is a coefficient of static friction. 52. The traction automatic adjustment planetary roller transmission according to claim 49, wherein the traction exceeds 0.3 and the surface hardness is higher than the Shore hardness A-90.   The traction self-adjusting planetary roller transmission according to claim 32, wherein an elastohydrodynamic lubricant is optionally contained in the transmission housing.

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