JPH06117511A - Wet machine type continuously variable transmission - Google Patents

Abstract

PURPOSE:To enable grease lubrication in a wet machine type continuously variable transmission, diversify mounting direction of the continuously variable transmission and to realize maintenance free. CONSTITUTION:In a continuously variable transmission of wet mechanic type (such type that power is transmitted using lubrication by traction transmission by its oil film), grease is used as a lubricating oil, a easing 114 is constituted so that it can be sealed, and a sun friction wheel 104, a planetary friction wheel 106 and a ring friction wheel 108 are all contained in a holder 110 in the almost cylindrical state. An opening 160 is formed in the holder 110 as a guide means for moving the grease to the center part of the holder 110, and the grease splashed on the holder inner circumference is raked and moved to the center part again by its end. As a result, stable lubrication can be done for a long time with a small amount of grease, efficiency is prevented from lowered even using grease with less fluidity than oil, and maintenance free is realized.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to two or more friction members frictionally engaged with each other through a lubricating oil in a casing.
The present invention relates to a wet mechanical type continuously variable transmission including a speed change mechanism that transmits rotation at a stepless speed ratio by making the effective rotation radius of at least one friction member variable.

[0002]

2. Description of the Related Art Conventionally, as this type of continuously variable transmission, for example, those shown in FIGS. 4 to 6, 7 or 8 and 9 are known.

In the continuously variable transmission shown in FIGS. 4 to 6, when the input shaft 2 is rotated by a motor (not shown), this rotation is caused by the three idlers 4 provided around the input shaft 2.
And the three spline shaft gears 6 are rotated via the three idlers 4. The reason why the rotation of the input shaft 2 is not directly transmitted to the spline shaft gear 6 is that the radial position of the spline shaft 8 changes due to the gear shifting operation, and this change must be absorbed by the idler 4.

When the spline shaft 8 is rotated by the rotation of the spline shaft gear 6, the cone disk 10 is rotated by this rotation, and the output shaft 14 is inserted through the flange disk 12 that is frictionally engaged while holding the cone disk 10. Rotates. In the illustrated conventional example, the flange disks 12 are arranged in the axial direction of the output shaft 14, and the cone disks 10 are equally arranged around the flange disks 12, and the flange disks 12 and the cone disks 10 are alternately arranged. It has a single-row or multi-row structure.

The flange disk 12 holds the cone disk 10 through the oil film 17 with an appropriate pressing force by the spring 16 (see FIG. 6), and each cone disk 1
0 (spline shaft 8) is displaceable in the radial direction, and this displacement changes the effective rotation radius of the cone disc 10 with respect to the flange disc 12, thereby changing the rotation speed ratio, that is, the gear ratio.

The radial displacement of the cone disk 10 (spline shaft 8) causes the slider 22 to move on the screw 20 by rotating the operating handle 18, as shown in FIG. The three pins 28 rotate around the center O in the direction of the arrow A via 26, and this rotation causes the three arms 32 to swing about the swing shaft 34 via the three rods 30, The spline shafts 8 respectively provided on the arms 32 move to the positions indicated by the symbol B, and the radial position from the center O of the cone disk 10 provided on the spline shafts 8 can be changed.

This speed change mechanism is substantially immersed in the oil (lubricating oil) put into the casing 35, and the power transmission by frictional engagement transmits the oil film 17 formed by this lubricating oil.
Done through. Reference numeral 36 in the drawing denotes an oil supply port for introducing the lubricating oil, 37 denotes an oil discharge port, and 38 denotes an oil gauge.

On the other hand, FIG. 7 shows a main structure of a wet mechanical continuously variable transmission disclosed in Japanese Patent Laid-Open No. 54-5164. The continuously variable transmission includes an input disk 42, a cone 44, a ring 46, which are integrally provided on the input shaft 40,
It is mainly composed of an output shaft 48 and a cam disk 50 connected thereto. When the input disk 42 integrated with the input shaft 40 rotates, the cone 44 revolves along the inner circumference of the ring 46 while rotating, and if the ring 46 is at the position P1, the cone 44 will rotate.
From the relationship of the contact radius between the ring 46 and the cam disk 50, 0 rotation (stop) is taken out to the output shaft 48, and when the ring 46 is moved in the P2 direction by the speed change operation, a differential phenomenon appears and the cam disk 50 gradually rotates. Start doing, P
Maximum rotation is obtained in 2 position. Even in this continuously variable transmission, although the differential rotation output is obtained due to the presence of the cam disk 50, the gear shifting itself is performed by the cone 44 and the ring 4.
This is done by changing the effective radius of gyration (of the cone 44) during frictional engagement with 6 and 6.

This transmission mechanism is also immersed in oil in a casing (not shown), and power is transmitted by frictional engagement through the oil (lubricating oil).

Next, FIGS. 8 and 9 show a conventional example in which a planetary engagement structure is adopted.

In this continuously variable transmission, power is transmitted through the thick chain line in FIG. That is, the rotation transmitted to the input shaft 70 is transmitted to the pair of sun friction wheels 74 including the fixed sun friction wheel 72 and the moving sun friction wheel 73. In the planetary friction wheel 76, the inner side of the disk portion is sandwiched by the disc friction spring 78 by the sun friction wheel 74, and the outer side thereof is fixed ring 8.
It is sandwiched by a ring friction wheel 82 composed of 0 and a moving cam 81. When the sun friction wheel 74 rotates, a planetary friction wheel 76
Revolves around the sun friction wheel 74 while rotating. The planet metal 86 attached to the groove of the carrier 84 takes out this revolution, and transmits it to the output shaft 88.

For speed change, the speed control shaft 90, the speed control nut 92, the ball head bolt 94, the ball retainer 96, etc. form a state as shown in FIGS.
The output shaft minimum rotation is obtained in the state (A), and the output shaft maximum rotation is obtained in the state (B). As is apparent from the figure, by moving the planetary friction wheel 76 in the radial direction, both the effective rotation radius of the planetary friction wheel 76 with respect to the sun friction wheel 74 and the effective rotation radius with respect to the ring friction wheel 82 are changed, As a result, the speed is changed in a stepless speed ratio.

Also in the case of this continuously variable transmission, the speed change mechanism is immersed in the oil of the casing (not shown), and the power is transmitted at the friction engagement portion using the oil as lubricating oil. .

As described above, the continuously variable transmission of the type in which the power is transmitted by the traction transmission force of the oil film using the lubricating oil is generally called a wet mechanical type continuously variable transmission. On the other hand, a continuously variable transmission that uses a belt and a pulley and does not use lubricating oil is called a dry mechanical continuously variable transmission. The present invention relates to a wet mechanical continuously variable transmission.

As a wet mechanical type continuously variable transmission, an extremely large number of structures have been proposed. However, since it is necessary to use parts having high hardness and high processing accuracy in the traction transmission part, it is currently the case. , Most of the wet mechanical type continuously variable transmissions have the above-mentioned three structures and their application systems are used.

[0016]

However, the conventional wet mechanical type continuously variable transmission uses a lubricating oil having a high traction coefficient, which is referred to as industrial gear oil 1 according to JIS K 2219 or traction oil. It was lubricated. Further, in the conventional wet mechanical type continuously variable transmission, in order to realize this oil lubrication, inevitably, an oil supply port, an oil discharge port, an air vent for preventing internal pressure due to stirring during operation,
Alternatively, it was necessary to install an oil gauge or the like to control the oil level. Therefore, when the design of these oil supply port, oil discharge port, air vent, oil gauge, etc. (hereinafter referred to as lubrication design) is performed in a preset mounting direction (for example, the direction of the output shaft is horizontal, downward, upward, etc.) However, there was a problem that this lubrication design had to be completely changed for a mounting direction different from this. That is, a transmission having a specific lubrication design can be mounted only in a specific direction, and therefore, there is a need for a type of transmission having a different lubrication design by the number of mounting directions to be secured.

Such a wet mechanical type continuously variable transmission lubrication system is becoming insufficient as a means of coping with the recent rationalization of the production system and the diversification of user requirements. There are various problems.

For example, in the field of a physical distribution system consisting of a plurality of conveyors, it is efficient to operate only the necessary parts of the physical distribution system when they are needed.
For this reason, each conveyor provided with a transmission can be independently driven.

In this case, each transmission mounted on the conveyor constitutes only a part of the conveyor, and this conveyor also constitutes a part of the entire physical distribution system. I'm just there. Therefore, in terms of the positional relationship with the entire physical distribution system, various mounting directions are required when mounting the transmission on each conveyor. That is, it has been required in one physical distribution system that the output shaft of the transmission is lateral, downward, upward, or oblique.

However, in order to improve the efficiency of maintenance of the entire system, it is convenient that the number of types of transmission is small. This means that there is a demand that the transmission should be used in various usage forms but not in many types.

Furthermore, in view of recent demands for cleaner working environment and maintenance-free equipment, maintenance-free requirements for wet-mechanical continuously variable transmissions of this type have been demanded.

However, as described above, the known wet-mechanical continuously variable transmission, whether it uses one type of industrial gear oil or traction oil, is different for different mounting methods. It is necessary to prepare a transmission with a lubrication design, and because it was manufactured with a design that requires regular oil changes, it is compatible with various mounting directions and is maintenance-free. The reality was that it wasn't done.

The present invention has been made in view of such a conventional problem, and is a wet mechanical type continuously variable transmission, and one type of transmission is applicable to various mounting directions. The purpose is to make it possible and to make this type of transmission maintenance-free.

[0024]

According to the present invention, the effective radius of rotation of at least one friction member among two or more friction members frictionally engaged with each other through lubricating oil in a casing is made variable, In a wet mechanical type continuously variable transmission equipped with a speed change mechanism that transmits rotation at a stepless gear ratio, grease is used as the lubricating oil, and the casing has a structure capable of being sealed, and at least the two or more frictions are provided. The above problem is solved by accommodating all the friction engagement parts of the member in a substantially cylindrical holder and forming guide means for moving the grease to the holder central portion side in the holder. Is.

[0025]

In order to solve the above-mentioned problems, the present invention can be developed for the first time by thoroughly examining the parts that have been conventionally regarded as common sense and have no doubt. In order to better understand the operation of the present invention, the development process will be described first.

Conventionally, it has been believed that "lubrication by oil" is essential for the generation of the oil film traction force of the traction transmission portion in the wet mechanical type continuously variable transmission. In addition, all continuously variable transmissions of this type that have been actually manufactured in the past have been manufactured based on this idea. That is, although some of the lubrication of the component parts may be grease lubrication, there has been no example in which the lubrication of the traction transmission portion (generation of oil film traction force) is grease lubrication.

However, the inventors of the present invention, in view of the fact that the grease lubrication and the sealing of the casing are indispensable in order to realize the maintenance-free mounting, which is possible in any mounting direction, anyway. Tried to lubricate with grease. Specifically, initially, a test was conducted using a wet mechanical type continuously variable transmission having the structure shown in FIGS. 4 to 6.

First, the applicability to the wet mechanical type continuously variable transmission was examined by the hardness of the grease. As a result, it has been experimentally found that grease consistency can be managed with the NLGI000 or NLGI00 consistency according to JIS K 2200, although the efficiency decrease and the temperature increase may increase.

The consistency means the apparent hardness of grease and the overall flow characteristics. More precisely, it is a value obtained by multiplying the depth (mm) in which the specified cone is fitted into the sample by 10 times. It is a representation. According to JIS K 2220, NLGI consistency numbers 000, 00, 0,
Consistency numbers 1 to 6 are shown. In addition,
NLGI is the National Lubricating Grease Inst
Abbreviation for itute (American Grease Society).

Next, the base oil constituting the grease was also tested in combination with various lubricating oils from high viscosity to low viscosity. As a result, experimentally, JI
If the industrial lubricating oil ISO viscosity grade ISO VG 10-150 mineral oil shown in SK2001 or a synthetic lubricating oil generally called a traction oil with an increased traction coefficient is used, good results in performance and life can be obtained. I found that.

Subsequently, the same test is performed on the wet mechanical continuously variable transmission having the structure shown in FIG. 7 or FIGS. 8 and 9, and the same test is performed on the properties of grease (combination of consistency and base oil). I was able to get the result.

However, in the structures of the above-mentioned three kinds of known transmission mechanisms, the efficiency is very low as compared with the oil lubrication, and the utility of the grease lubrication can be obtained only as it is denied. . Then, the inventors conducted a follow-up investigation on the cause of the decrease in efficiency and found the following facts.

That is, since grease is less fluid than oil, it tends to scatter and collect on the inner peripheral surface of the casing due to the engagement of the friction wheel of the traction transmission section. Therefore, in order to obtain flexibility in the mounting direction, which is one of the major purposes of grease lubrication in this state, even if the scattered grease collects on the inner peripheral surface of the casing, it is necessary to secure the grease in the traction transmission section. I won't. This means that as a result, it is necessary to put a considerable amount of grease in the casing, and as a result, it is considered that the stirring loss is increased and the efficiency is reduced.

Specifically, in the case of the speed change mechanism shown in FIGS. 4 to 6, since the traction transmission portion is opened (there is no particular problem in the case of oil lubrication), the grease is likely to be scattered, and the scattered grease is also removed. It was observed that the grease could not be recovered and the grease gradually disappeared in the most lubricated central part.

Further, in the structure shown in FIG. 7, since the cone 44 rotates and revolves around the cone 44, the engaging portion moves largely in the casing, and therefore the grease is required to ensure lubrication at all engaging portions. It was necessary to add a large amount of P., resulting in a large stirring loss. Further, also in this structure, since there is no means for scraping off the grease scattered around the outer periphery, it has been found that the grease in the vicinity of the central portion gradually decreases.

Further, in the structure of FIGS. 8 and 9, the traction transmission portion is located on the outer peripheral side in the radial direction and the planetary friction wheel 7 is used.
Since 6 is a carrier type planetary structure that rotates and revolves, the engaging portion between the planetary friction wheel 76 and the ring friction wheel 82 moves greatly in the casing, and therefore the same structure as that of FIGS. Something went wrong. There is also a problem in that a large amount of grease must be added due to the structure, particularly when the output shaft 88 faces downward.

In view of such a point, the inventors have adopted grease as a lubricating oil and have a structure capable of sealing a casing, and further, all the friction engaging portions of the friction member have a substantially cylindrical holder. The holder is provided with a guide means for moving the grease toward the center of the holder.

As a result, it is possible to eliminate the conventional concept of lubrication design such as the oil supply port, the oil drain port, the air vent, the oil gauge, and the like, and it is possible to mount in any direction. Also, maintenance-free has been realized.

Since the frictional engagement portion is housed in the cylindrical holder and the holder is provided with the guide means for moving the grease to the central portion, the scattered grease can be always pushed back to the central portion side. This is because it is possible to always secure the grease in the friction engagement portion without adding a large amount of grease, and it is possible to minimize the decrease in efficiency.

The structure of the speed change mechanism is as follows: a pair of sun friction wheels connected to the input shaft, and a planet that is held by the pair of sun friction wheels at an arbitrary radial position and frictionally engages with the sun friction wheels. A friction wheel and a pair of ring friction wheels that are inscribed and engaged with the planet friction wheel while sandwiching the friction wheel are provided, and a carrier that supports the planet friction wheel is fixed so that only the planet friction wheel rotates. It is preferable that the ring friction wheel is connected to the output shaft while being performed (claim 2). As a result, the friction member itself of the speed change mechanism does not move significantly (revolution etc.), so that stirring loss etc. can be suppressed to the minimum even if grease having less fluidity than conventional oil is used. become.

Further, if the holder is constructed so as to rotate integrally with the output shaft, it is favorable since it is not necessary to additionally provide a power transmission means for rotating the holder (claim 3).

The holder does not necessarily have to rotate itself. For example, the rotation of the friction member adjacent to the holder causes the grease to receive a reaction force from the guide plate provided on the holder and move to the center of the holder. It may be configured as described above.

Needless to say, this holder may be configured to be rotated via a separate speed reducing mechanism by utilizing the rotation of the input shaft, for example. In this way, if a separate holder drive mechanism that is synchronized with the rotation of the input shaft is provided, the output shaft rotation may be changed to almost zero as in the conventional example described in FIG. However, the holder can be surely rotated. In this case, since the torque for rotating the holder may be small, for example, a speed reducing mechanism such as a cyclo speed reducer (registered trademark of the applicant) having an extremely small axial thickness may be adopted.

Further, the grease moving guide means has a simple structure if, for example, an opening is formed in the outer peripheral portion of the holder and the end of the opening has the function of the guide means. In addition, the guide means can be formed at low cost (claim 4).

The consistency of the grease may be either 000 or 00 as the NLGI consistency number in JIS K 2220, which has relatively fluidity as described above (claim 5). This is a conclusion drawn from the applicant's enormous experimental results.

The base oil of the grease is JIS K
The industrial lubricating oil ISO viscosity grade ISO 10 to 150 mineral oil shown in 2001, and the synthetic lubricating oil having an increased traction coefficient are preferable (claim 6). This is also a conclusion drawn based on the applicant's experimental results.

[0047]

Embodiments of the present invention will now be described in detail with reference to the drawings.

1 to 3 show a wet mechanical type continuously variable transmission to which the present invention is applied.

This continuously variable transmission adopts a planetary engagement structure as its speed change mechanism. In FIG. 1, 102 is an input shaft, 104 is a pair of sun friction wheels, 106 is a planetary friction wheel, 108 is a pair of ring friction wheels, 110 is a holder, 1
12 is an output shaft, and 114 is a casing.

A spline shaft 120 is arranged at the tip of the input shaft 102, and the pair of sun friction wheels 104 are attached to the spline shaft 120. The sun friction wheel 104 holds the planetary friction wheel 106 with a predetermined pressure by a disc spring 122. The planetary friction wheel 106 shown on the upper side of FIG. 1 shows the case where the effective radius of the planetary friction wheel 106 with respect to the sun friction wheel 104 is large, and the planetary friction wheel 106 shown on the lower side shows the case where this is small. There is.

As is apparent from the figure, in this embodiment,
The sum of the axial lengths of the disc spring 122 and the sun friction wheel 104 is restricted to L by the pair of retaining rings 124 and 126. Therefore, when the planetary friction wheel 106 is deeply inserted into the sun friction wheel 104. In the case of the lower side of the figure, a stronger holding force is applied from the disc spring 122.

As shown in FIG. 2, three planetary friction wheels 106 are provided around the sun friction wheel 104. When the operation handle 128 is rotated, the worm shaft 130 rotates and the worm wheel 133 rotates. However, the three pins 138 rotate around the center O. On the other hand, the rotation shaft 140 of the planetary friction wheel 106 can move on a long hole formed long in the radial direction. The rotation shaft 140 of the planetary friction wheel and the above-described three pins 138 are connected by three rods 142, respectively, and as a result, the rotation of the pin 138 around the center O causes the rotation shaft 140 to move in the radial direction. You can make a round trip.

The planetary friction wheels 106 are engaged with the ring friction wheels 108, respectively. This ring friction wheel 108
The retaining ring 1 is provided on the inner peripheral side of the holder 110.
50 and the coil spring 152, the planetary friction wheel 106
Is engaged by holding it at a predetermined pressure.

The upper side of the figure shows the case where the effective radius of the planetary friction wheel 106 with respect to the ring friction wheel 108 is small, while the lower side of the figure shows the case where it is large.

As shown in FIG. 3, the holder 110 has a substantially cylindrical shape, and four openings 160 are formed in this embodiment. Further, the end portion 162 is cut slightly obliquely so that the grease accumulated in the vicinity of the outer periphery can be moved to the central portion as if scraped off during rotation. This holder 110 has one end of the cylinder closed, and the output shaft 1
12 (FIG. 1).

On the other hand, the casing 114 covers the entire transmission mechanism so as to be hermetically sealed, and the casing 11
The space formed by 4 is filled with grease, not conventional oil, to such an extent that the frictional engagement portions of the sun friction wheel 104 and the planetary friction wheel 106 in the central portion are covered.

The consistency of this grease is JIS
The NLGI consistency number in K 2220 is 000. Note that NLGI00 may be practically used.

The viscosity of the base oil of grease is JIS
The industrial lubricating oil ISO viscosity grade shown in K 2001 is ISO VG 10-150. This is because it is recognized that the grease of this property is the most efficient and has the property that it can perform good traction transmission for a long period of time.

Next, the operation of the apparatus of this embodiment will be described.

The rotation of the input shaft 102 is performed by the spline shaft 12
It is transmitted to the sun friction wheel 104 via 0, and further transmitted to the three planetary friction wheels 106.

Since the planetary friction wheel 106 is of a so-called star type in which the shaft does not revolve, the planetary friction wheel 106 only rotates and the ring friction wheel 108 frictionally engaged with it by this rotation. Rotates. Since the ring friction wheel 108 is fixed to the holder 110, the rotation of the ring friction wheel 108 is the rotation of the holder 110, and the output shaft 112 rotates.

Here, since the rotation shaft 140 of the planetary friction wheel 106 is movable in the radial direction, the effective radius of the planetary friction wheel 106 with respect to the sun friction wheel 104 and the ring friction wheel 108 is thereby changed. It can be changed at the same time, and the overall gear ratio can be changed steplessly.

By the way, in the speed change mechanism according to this embodiment, among the sun friction wheel 104, the planetary friction wheel 106, and the ring friction wheel 108, the grease of the sun friction wheel 104 easily scatters and the lubrication condition is the most severe. Become. However,
In this embodiment, the sun friction wheel 104 is arranged at the center in the radial direction, and the grease is always collected in the central portion as the holder 110 rotates. Therefore, the lubrication of this portion can be performed very well. it can. That is, since the holder 110 always rotates during operation, the grease scattered by the rotation of the sun friction wheel 104 and the planetary friction wheel 106 is once received by the inner peripheral surface of the holder 110 to perform lubrication there. Opening 160 of holder 110
With the rotation of the holder 110 by the guide function of the (end portion 162), the collected grease is scraped and moved again to the central portion side of the holder, so that efficient lubrication can be performed for a long time even with a small amount of grease. .

In this embodiment, the ring friction wheel 108 is also used.
However, since the holder 110 is made to perform the function of this connecting member, the number of parts can be reduced accordingly.

In this embodiment, a planetary engagement structure in which the planetary friction wheel 106 only revolves without revolving is adopted as the speed change mechanism, and the stirring loss is reduced as much as possible. In the present invention, the structure itself of the speed change mechanism is not particularly limited to the structure of this embodiment, and for example, various conventionally known speed change mechanisms may be adopted as they are.

In this case, for example, in the case of the structure shown in FIGS. 4 to 6, for example, the idler 4 is rotated once more.
It is possible to adopt a structure in which the cylindrical holder is rotated after the speed is reduced. Further, in the case of the conventional example as shown in FIG. 7, it is preferable to provide a cylindrical holder on the outer peripheral side of the ring 46 so as to receive the rotational power directly reduced from the input shaft 40, for example. This allows the output shaft 48
The holder can be rotated even when the rotation of the holder becomes zero.

Further, in the case of the transmission mechanism as shown in FIG. 8, for example, a holder configured to rotate by an appropriate method is provided at the outer peripheral position of the planetary friction wheel 76 and the ring friction wheel 82. Good.

As described above, in the present invention, the structure itself of the planetary gear mechanism is not particularly limited.

[0069]

As described above, according to the present invention, the conventional lubrication with oil is used, and therefore, the continuously variable transmission having a specific lubrication design is mounted only in the direction conforming to the lubrication design. Although this was not possible, the present invention allows mounting in either direction. Also, since grease that has less fluidity than oil is used as the material for the lubricating oil, the grease scattered by the holder and the guide means can be returned to the central part again, so the amount of grease input can be reduced It is possible to maintain good lubrication for a long period of time while reducing stirring loss, and to realize maintenance-free operation.

[Brief description of drawings]

FIG. 1 is a sectional view showing a wet mechanical type continuously variable transmission to which the present invention is applied.

FIG. 2 is an explanatory view showing a configuration for moving a support shaft of a planetary friction wheel in a radial direction.

FIG. 3 is a perspective view showing an overall schematic appearance of a holder.

FIG. 4 is a cross-sectional view showing an example of a conventional wet mechanical type continuously variable transmission.

FIG. 5 is an arrow V for explaining the shifting operation of the conventional example.
-Cross sectional view along line V

FIG. 6 is an enlarged sectional view showing an engaged state of the flange disc and the cone disc.

FIG. 7 is a cross-sectional view showing the main parts of another example of a conventional wet mechanical type continuously variable transmission.

FIG. 8 is a sectional view showing a main part of still another example of a conventional wet mechanical type continuously variable transmission.

9 is a cross-sectional view showing a shift form of the continuously variable transmission shown in FIG.

[Explanation of symbols]

 102 ... Input Shaft 104 ... Sun Friction Wheel 106 ... Planetary Friction Wheel 108 ... Ring Friction Wheel 110 ... Holder 112 ... Output Shaft 114 ... Casing

Claims (6)

[Claims] Claim: What is claimed is: 1. By changing the effective rotation radius of at least one friction member of two or more friction members frictionally engaged with each other through lubricating oil in the casing, the rotation can be performed at a stepless speed ratio. In a wet mechanical continuously variable transmission having a transmission mechanism for transmitting, a grease is used as the lubricating oil, and the casing has a structure capable of being sealed, and at least all friction engagement portions of the two or more friction members. Is housed in a substantially cylindrical holder, and a guide means for moving the grease to the holder central portion side is formed in the holder, a wet mechanical type continuously variable transmission. 2. The pair of sun friction wheels connected to an input shaft, and the pair of sun friction wheels sandwiched between the pair of sun friction wheels at an arbitrary radial position to frictionally contact the sun friction wheels. The planetary friction wheel is provided with an engaging planetary friction wheel and a pair of ring friction wheels that are inscribed and engaged with the planetary friction wheel while holding the planetary friction wheel, and a carrier that supports the planetary friction wheel is fixed. A wet-mechanical continuously variable transmission, characterized in that the ring friction wheel is connected to an output shaft while rotating only. 3. The wet mechanical continuously variable transmission according to claim 1, wherein the holder rotates integrally with the output shaft. 4. The opening according to any one of claims 1 to 3, wherein an opening is formed in an outer peripheral portion of the holder, and an end portion of the opening has a function of a guide unit for moving the grease. Wet mechanical type continuously variable transmission. 5. The consistency according to claim 1, wherein the grease has a consistency of NL according to JIS K2220.
A wet mechanical continuously variable transmission characterized by having a GI consistency number of either 000 or 00. 6. The grease according to claim 1, wherein the grease base oil is an industrial lubricating oil ISO viscosity grade ISO VG 10-1 according to JIS K2001.
A wet mechanical continuously variable transmission, characterized in that it is one of 50 mineral oils and a synthetic lubricating oil with an increased traction coefficient.