JP2004019727A - Frictional roller type transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To inhibit transmission of torsional vibration to a high-speed rotating machine by reducing the transmission of rotating fluctuation to a speed-up gear. <P>SOLUTION: A low speed-side shaft 3 is rotatably supported on a housing 1, an outer ring 32 is mounted on one end part of the low speed-side shaft 3, and a high speed-side shaft 17 is rotatably supported in a state of being eccentric to the low speed-side shaft 3 and the outer ring 32. Two guide rollers 37a, 37b and a movable roller 38 moving in transmitting the torque are mounted between the outer ring 32 and the high speed-side shaft 17. A pulley P incorporating a one-way clutch Y is used for the low speed-side shaft 3 (input side) of a wedge roller-type transmission A. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a friction roller type transmission utilizing a wedge effect which is suitable for a machine in which a high-speed side shaft rotates at a high speed, for example, a turbomachine, a supercharger, a speed increasing machine such as a machine tool.
[0002]
[Prior art]
In JP-A-4-203421 and JP-A-11-294548, a supercharger for a vehicle engine is of a centrifugal type, in which power is transmitted directly from an engine drive shaft to a belt, and is increased by a gearbox. At a high speed, the impeller is rotationally driven.
[0003]
In JP-A-4-203421, a planetary gear mechanism is used as a speed increasing device in order to obtain a high speed increasing ratio. However, at a rotational speed ranging from tens of thousands to more than 100,000 rpm, there is a serious problem in terms of life as well as gear vibration and noise.
[0004]
Japanese Patent Application Laid-Open No. H11-294548 discloses a method using a planetary roller of a friction roller mechanism. By tightening a planetary roller and a sun shaft with a flexible outer ring, a pressing force required by a traction drive is reduced. Structure. Therefore, slip occurs in a high rotation and high torque state, and the driving force cannot be transmitted to the impeller. In order to prevent this, it is necessary to tighten the planetary roller with the outer ring with a larger force, but in such a case, in a low rotation and low torque state, the pressing is performed with an excessive pressing force, and the efficiency is reduced. I will. At the same time, since a large pressing force always acts, there is a problem in terms of life.
[0005]
[Problems to be solved by the invention]
Further, as described above, in the system in which power is directly obtained from the drive shaft (crankshaft) of the engine by belt transmission, the rotation of the crankshaft of the engine varies according to the number of cylinders due to ignition and combustion of the engine. have. Therefore, rotation fluctuations are input to the pulley of the gearbox driven from the crankshaft of the engine. Since the speed is increased by the speed increaser, the rotation fluctuation of the engine is amplified on the impeller side. Due to the amplified rotation fluctuation (vibration), a large torsional vibration is applied to the impeller and the output shaft, so that the strength of the impeller and the output shaft may be insufficient.
[0006]
As described above, the problem caused by the rotation fluctuation caused by the ignition and combustion of the engine is more remarkable because the speed increaser increases the speed from tens of thousands rpm to 100,000 rpm or more.
[0007]
In addition, since the rotation increased in speed by the belt enters the pulley of the speed increaser, the rotation fluctuation of the engine is also amplified here.
[0008]
The present invention has been made in view of the above-described circumstances, and utilizes a wedge effect that reduces transmission of rotational fluctuation to a speed-increasing gear and suppresses transmission of torsional vibration to a high-speed rotating machine. An object of the present invention is to provide a friction roller type transmission.
[0009]
[Means for Solving the Problems]
In order to achieve the above object, a friction roller type transmission utilizing a wedge action according to claim 1 of the present invention rotatably supports a low speed side shaft in a housing, and has an outer ring at one end of the low speed side shaft. On the other hand, eccentric with respect to the low-speed side shaft and the outer ring, rotatably support the high-speed side shaft,
At least one guide roller and at least one movable roller that moves during torque transmission between the outer ring and the high-speed side shaft,
The low-speed side shaft is provided with a pulley via a one-way clutch.
[0010]
Further, the friction roller type transmission utilizing a wedge action according to claim 2 rotatably supports a low-speed side shaft in a housing and provides an outer ring at one end of the low-speed side shaft, while the low-speed side shaft and the low-speed side shaft are provided. Eccentric to the outer ring, rotatably supporting the high-speed side shaft,
At least one guide roller and at least one movable roller that moves during torque transmission between the outer ring and the high-speed side shaft,
The low-speed side shaft is provided with a pulley via a torsional damper.
[0011]
As described above, according to the present invention, the friction roller type transmission utilizing the wedge action is used as a speed increasing device of a high-speed rotating machine, and the wedge roller type transmission is a traction drive, and is quiet even at high speed rotation. Since smooth power transmission can be performed, there is no problem of vibration and noise. Further, the pressing force required for the traction drive is a mechanism obtained by a wedge action, and an appropriate pressing force proportional to the transmission torque is always obtained, so that no slip occurs. At the same time, high efficiency is obtained from the low rotation and low torque region to the high rotation and high torque region.
[0012]
Further, the low-speed side shaft includes a pulley via a one-way clutch, or includes a pulley via a torsional damper.
[0013]
Therefore, for example, since the rotational fluctuation from the engine or the like is reduced and input to the wedge roller type transmission, the rotational fluctuation in the transmission is reduced, and the torsional vibration applied to the high-speed rotating machine is suppressed. The possibility that the output shaft of the high-speed rotating machine becomes insufficient in strength can be eliminated. Note that a diesel engine is particularly effective because the engine rotation fluctuation is large.
[0014]
The traction drive type transmission has been developed for various industrial uses because of its quietness and smoothness. In recent years, attempts have been made to apply it to personal use such as automobiles and bicycles, and it has attracted attention as a next-generation power transmission system. ing.
[0015]
A traction drive type transmission is different from a gear transmission in that at least two rotating bodies having a smooth surface are strongly pressed and a lubricating oil film (for example, an EHL oil film) is interposed therebetween to transmit power. The basic formula is represented by a simple friction formula of Ft = μ · Fc (Ft: traction force). Here, Fc is called a pressing force, and various methods have been developed for generating the pressing force.
[0016]
As one of the traction drive type transmissions, there is a friction roller type transmission utilizing a wedge action (hereinafter referred to as a wedge roller type transmission). The wedge roller type transmission includes an outer ring rotatably provided around an end of a high speed side shaft in an eccentric state with respect to the high speed side shaft, and a driven side which is an outer peripheral surface of the high speed side shaft. A power transmission is provided between the cylindrical surface and the drive-side cylindrical surface that is the inner peripheral surface of the outer ring, and is arranged in an annular space whose radial width is not uniform in the circumferential direction. A transmission having at least one guide roller and at least one movable roller as a cylindrical surface for use. The movable roller is a roller that generates a pressing force by a wedge action, and is a roller that moves in a radial direction and a circumferential direction.
[0017]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, a wedge roller type transmission according to an embodiment of the present invention will be described with reference to the drawings.
[0018]
FIG. 1 is a sectional view of a wedge roller type transmission according to an embodiment of the present invention. FIG. 2 is a cross-sectional view of the wedge roller type transmission having a one-way clutch function along the line bb in FIG. 1, FIG. 3 is a diagram illustrating the operation of the wedge roller type transmission, and FIG. It is sectional drawing of the wedge roller type transmission which can transmit a torque at the time of rotation of both reverse directions.
[0019]
In the present embodiment, the wedge roller type transmission A functions as a speed increase gear having the low speed side shaft 3 (outer ring side) as an input side and the high speed side shaft 17 as an output side. However, the present invention is also applicable to a speed reducer having a low-speed side shaft (outer ring side) as an output side.
[0020]
Also, as shown in FIG. 2, the wedge roller type transmission A has a one-way clutch function that transmits torque during forward rotation, but does not transmit torque when rotating reversely, As shown in FIG. 7, torque may be transmitted during both forward and reverse rotations.
[0021]
In a wedge roller type transmission A according to an embodiment of the present invention, a housing 2 which is a partition plate is fixed to a substantially cylindrical housing 1 in FIGS. A low-speed side shaft 3 is rotatably supported by the housing 1, and a disk-shaped member 4 is provided at an end of the low-speed side shaft 3 in the housing 1. An outer ring 32 is attached.
[0022]
The high-speed side shaft 17 is eccentrically (offset) with respect to the low-speed side shaft 3 and the outer ring 32 and is rotatably provided in the housing 2 serving as a partition plate.
[0023]
As shown in FIG. 2, a large-diameter guide roller 37a, a small-diameter guide roller 37b, and a movable roller 38 that moves during torque transmission are interposed between the outer ring 32 and the high-speed side shaft 17. is there.
[0024]
As shown in FIG. 3, the support shaft 39 b that rotatably supports the movable roller 38 is configured to be movable between the high-speed side shaft 17 and the outer ring 32 in a direction that bites into a “wedge”. It is urged by an elastic member 47 (see FIG. 2) such as a compression spring installed in the cylinder hole 46 in a direction to bite into the “wedge”.
[0025]
As a result, as shown in FIG. 3, during normal rotation, the movable roller 38 moves between the high-speed side shaft 17 and the outer ring 32 in a direction to bite into a “wedge”, and generates a pressing force Fc. A traction force is generated by this Fc, and torque can be transmitted.
[0026]
On the other hand, at the time of reverse rotation, the movable roller 38 moves in a direction away from the “wedge”, the pressing force Fc becomes zero, the outer ring 32 idles, and the torque cannot be transmitted to the high-speed side shaft 17.
[0027]
As shown in FIG. 2, between the inner peripheral surface of the outer race 32 and the outer peripheral surface of the distal end portion of the high-speed shaft 17, there is provided an annular space 36 whose radial width is not uniform in the circumferential direction.
[0028]
In the annular space 36, two guide rollers 37a and 37b and one movable roller 38 are installed to constitute the wedge roller type transmission A. In the figure, the movable roller 38 is partially cut away. Three support shafts 39a, 39a, 39b are provided in the annular space 36 for installing these rollers 37a, 37b, 38. Of the three support shafts 39a, 39a, 39b, the two support shafts 39a, 39a are press-fitted and fixed at both ends to fitting holes 40, 40 formed in the housing 2 and the connecting plate 14. . Therefore, the two support shafts 39a, 39a are not displaced in the circumferential direction or the diametric direction in the annular space 36. On the other hand, of the three support shafts 39a, 39a, 39b, the other one of the support shafts 39b located on the upper left side of FIG. The outer ring 32 is supported so as to be slightly displaceable in the circumferential and diametric directions. For this purpose, a support hole 41 having an inner diameter larger than the outer diameter of the support shaft 39b is formed in a part of the housing 2 and the connecting plate 14 which is aligned with both ends of the one support shaft 39b. Both ends of the support shaft 39b are loosely engaged with these support holes 41.
[0029]
The guide rollers 37a, 37b and the movable roller 38 are respectively mounted around the intermediate portions of the support shafts 39a, 39a, 39b supported as described above, by bearings such as radial needle bearings 42, 42, respectively. The bearing is rotatably supported by a bearing (not shown). In order to connect and fix the connecting plate 14 to the housing 2, projections 27, 27 protruding from one surface of the connecting plate 14 are respectively provided with the guide rollers 37 a with respect to the circumferential direction of the connecting plate 14. , 37b and the movable roller 38. In other words, each of the protrusions 27 and 27 and each of the guide rollers 37a and 37b or the movable roller 38 are present alternately in the annular space 36 in the circumferential direction of the annular space 36. In addition, the outer peripheral surface of each of the guide rollers 37a, 37b or the movable roller 38 does not interfere with (rub against) the circumferential side surface of each of the protrusions 27, 27.
[0030]
In this manner, the power transmission, which is the outer peripheral surfaces of the guide rollers 37a, 37b and the movable roller 38, which are rotatably supported between the housing 2 and the connecting plate 14 by the support shafts 39a, 39a, 39b, respectively. The driving cylindrical surfaces 43a, 43a, 43b are respectively brought into contact with a driven cylindrical surface 44, which is the outer peripheral surface of the distal end portion of the high-speed shaft 17, and a driving cylindrical surface 45, which is the inner peripheral surface of the outer ring 32. ing. As described above, the width in the radial direction of the annular space 36 in which the guide rollers 37a and 37b and the movable roller 38 are installed is not uniform in the circumferential direction. As described above, the outer diameters of the guide rollers 37a and 37b and the movable roller 38 are made different by the amount of making the width of the annular space 36 unequal in the circumferential direction. That is, of the guide rollers 37 a and 37 b and the movable roller 38, the movable roller 38 and the guide roller 37 b which are located on the side where the tip of the high speed side shaft 17 is eccentric with respect to the outer ring 32 (upper side in FIG. 2). The outer diameters are the same and relatively small. On the other hand, the outer diameter of the guide roller 37a located on the opposite side (lower side in FIG. 2) of the tip of the high-speed shaft 17 to the outer ring 32 is set to the movable roller 38 and the guide roller 37b. It is larger than the outside diameter. The power transmission cylindrical surfaces 43a, 43a, 43b, which are the outer peripheral surfaces of the guide rollers 37a, 37b and the movable roller 38, are brought into contact with the driven side and drive side cylindrical surfaces 44, 45, respectively. .
[0031]
Note that, of the guide rollers 37a and 37b and the movable roller 38, both ends of the support shafts 39a and 39a that support the guide rollers 37a and 37b respectively (as described above) with respect to the housing 2 and the connecting plate 14. (Within the annular space 36). On the other hand, the support shaft 39b supporting the movable roller 38 causes a slight displacement in the circumferential direction and the diametric direction with respect to the housing 2 and the connecting plate 14 (in the annular space 36) as described above. We support as much as possible. Therefore, the movable roller 38 can also be slightly displaced in the annular space 36 in the circumferential direction and the diametric direction. The support shaft 39b supporting the movable roller 38 is rotatably supported on the support shaft 39b by an elastic member 47 such as a compression spring installed in the cylinder hole 46 of the housing 2 and the connecting plate 14. The roller 38 is elastically lightly pressed so as to move the roller 38 toward the narrow portion of the annular space 36.
[0032]
When the rotating shaft is rotationally driven by the wedge roller type transmission according to the present invention configured as described above, a driving force is input to the low-speed side shaft 3 to rotate the outer ring 32 clockwise in FIG. . The rotation of the outer ring 32 is transmitted to the high-speed side shaft 17 via the guide rollers 37a and 37b and the movable roller 38, and rotates the high-speed side shaft 17 counterclockwise in FIG. The power transmission between the outer ring 32 and the guide rollers 37a and 37b and the movable roller 38 and the power transmission between the guide rollers 37a and 37b and the movable roller 38 and the high-speed shaft 17 are all frictional. Since transmission is performed, noise and vibration generated during power transmission are low.
[0033]
Further, the movable roller 38 tends to bite into the narrow portion (the upper central portion in FIG. 2) of the annular space 36 with a force corresponding to the magnitude of the torque transmitted from the outer ring 32 to the high-speed shaft 17. It becomes. Therefore, a contact portion between the drive-side cylindrical surface 45, which is the inner peripheral surface of the outer ring 32, and the power transmission cylindrical surfaces 43a, 43a, 43b, which are the outer peripheral surfaces of the guide rollers 37a, 37b and the movable roller 38, and The surface pressure of the contact portion between each of the power transmission cylindrical surfaces 43a, 43a, 43b and the driven-side cylindrical surface 44, which is the outer peripheral surface of the high-speed shaft 17, is higher as the torque is larger. Become. Conversely, when the torque is small, the surface pressure of each contact portion is low. For this reason, the torque can be efficiently transmitted by setting the surface pressure of each contact portion to an appropriate value corresponding to the torque to be transmitted.
[0034]
That is, when the outer ring 32 rotates clockwise in FIG. 2 and the high-speed side shaft 17 also rotates counterclockwise in the same manner, the movable roller 38 is driven by the driving cylinder, which is the inner peripheral surface of the outer ring 32. By receiving a force in the same direction as the pressing force by the elastic member 47 from the surface 45 and the driven-side cylindrical surface 44 which is the outer peripheral surface of the high-speed side shaft 17, the annular space 36 has a narrow portion, that is, FIG. 2 tends to move toward the upper center.
[0035]
As a result, the power transmission cylindrical surface 43b, which is the outer peripheral surface of the movable roller 38, strongly presses the drive side cylindrical surface 45 and the driven side cylindrical surface 44. An inner diameter side contact portion 48, which is a contact portion between the power transmission cylindrical surface 43b and the driven cylindrical surface 44, and a contact between the power transmission cylindrical surface 43b and the drive side cylindrical surface 45. The contact pressure of the outer diameter side contact portion 49, which is the contact portion, increases. As described above, when the contact pressure of the inner and outer contact portions 48 and 49 with respect to the movable roller 38 increases, the movable roller 38 is pressed by the power transmission cylindrical surface 43b which is the outer peripheral surface of the movable roller 38. The high-speed side shaft 17 and the outer ring 32 are slightly displaced in the diameter direction due to elastic deformation and assembling clearance. As a result, the contact pressure of both the inner and outer contact portions 48 and 49 with respect to the guide rollers 37a and 37b increases. The rotational force of the outer ring 32 is transmitted to the high-speed shaft via the guide rollers 37a and 37b and the movable roller 38 based on the frictional engagement between the inner and outer diameter contact portions 48 and 49. 17 can be freely transmitted.
[0036]
As described above, the force for moving the movable roller 38 toward the narrow portion of the annular space 36 depends on the magnitude of the rotational driving force transmitted from the outer ring 32 to the high-speed side shaft 17. Change. The greater the force, the higher the contact pressure between the inner diameter side and the outer diameter side contact portions 48, 49. Therefore, based on such an operation, the contact pressure according to the transmitted rotational driving force is automatically selected, and the transmission efficiency of the wedge roller type transmission A can be secured.
[0037]
In the case of the example shown in FIG. 2, the wedge roller type transmission A has a one-way clutch function, and the rotation speed of the high-speed side shaft 17 matches the rotation speed of the outer ring 32, that is, this outer ring If the rotation speed of the wedge roller type transmission A becomes higher than the rotation speed of the wedge roller type transmission A, the connection of the wedge roller type transmission A is disconnected. That is, in this case, the movable roller 38 is displaced toward the wide side (the lower left side in FIG. 2) of the annular space 36 against the elasticity of the elastic member 47. As a result, the contact pressure between the inner diameter side and the outer diameter side contact portions 48 and 49 is reduced or lost, and the rotation of the outer ring 32 is not transmitted to the high speed side shaft 17.
[0038]
Next, a wedge roller type transmission shown in FIG. 4 that can transmit torque when rotating in both forward and reverse directions will be described.
[0039]
FIG. 4 shows a structure in which the high-speed shaft 17 (see FIG. 1) is rotatable in both clockwise and counterclockwise directions. Therefore, the structure of the present embodiment is implemented in combination with a high-speed rotating machine X (see FIG. 1) whose rotation direction can be freely changed. In such a configuration of the present example, one guide roller 37 and two movable rollers 38a and 38b are used as the three rollers constituting the wedge roller type transmission A. . Among them, the roller installed in the widest part of the annular space 36 is a guide roller 37 having a relatively large diameter and the installation position does not change. On the other hand, a pair of rollers provided so as to sandwich the portion where the width of the annular space 36 becomes the narrowest is a movable roller 38a which has a relatively small diameter and enables a slight displacement in the circumferential and diametric directions. , 38b. The support shafts 39b and 39b supporting the movable rollers 38a and 38b are elastically pressed toward the narrowest portion of the annular space 36, respectively.
[0040]
In the case of the structure of the present example configured as described above, when the outer ring 32 rotates clockwise in FIG. 4, the movable roller 38a on the left side in FIG. Bite into. On the other hand, when the outer ring 32 rotates in the counterclockwise direction in FIG. 4, the movable roller 38b on the right side in FIG. 4 bites into the narrowed portion of the annular space 36. Further, in the case of this example, in order to support both ends of the support shafts 39b, 39b supporting the movable rollers 38a, 38b, the annular shape of the support holes 41a, 41a formed in the housing 2 and the connecting plate 14 is set. The length of the space 36 in the circumferential direction is regulated. More specifically, the position of the end of each of the support holes 41a, 41a on the side where the width of the annular space 36 is wide (the lower side in FIG. 4) is more than that in the case shown in FIG. The annular space 36 is brought closer to the position where the width is narrowest. The movable rollers 38a and 38b are prevented from retreating excessively to the wide side of the annular space 36.
[0041]
In the case of the present embodiment configured as described above, even when the outer ring 32 rotates in any of the clockwise and counterclockwise directions, any of the movable rollers 38a (38b) is a part of the annular space 36 having a narrow width. And the contact pressure of the contact portions 48 and 49 on the inner diameter side and the outer diameter side with respect to the movable roller 38a (38b) is increased. On the other hand, the retractable amount of the movable roller 38b (38a) displaced in the direction of retracting from the narrow portion of the annular space 36 is also limited. As a result, with respect to both the movable rollers 38a, 38b and the guide roller 37, the contact pressures of the contact portions 48, 49 on the inner diameter side and the outer diameter side are sufficiently increased, and from the outer ring 32 to the high speed side shaft 17, Motion can be transmitted efficiently. As described above, except that the power transmission from the rotating outer ring 32 to the high-speed side shaft 17 in both the clockwise and counterclockwise directions is enabled, the configuration is the same as that described above with reference to FIG. Omitted.
[0042]
(1st Embodiment)
Next, a first embodiment will be described. FIG. 1 is a sectional view of a wedge roller type transmission according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view of the wedge roller type transmission having a one-way clutch function along the line bb in FIG. 1, FIG. 3 is a diagram illustrating the operation of the wedge roller type transmission, and FIG. It is sectional drawing of the wedge roller type transmission which can transmit a torque at the time of both reverse rotation. FIG. 5 is an enlarged sectional view of an example in which two angular ball bearings are combined in front.
[0043]
In the hole 23 of the partition plate (housing) 2, a pair of angular ball bearings 24, 25 in which two are assembled in front are interposed, and are firmly fixed together with a seal member 29 by a preload member 26. The preload member 26 presses the outer races of the bearings 24 and 25 in the axial direction to apply a preload so as to eliminate a clearance inside the bearing.
[0044]
No bearing is provided on the high-speed rotating machine X side. This is because if the high-speed side shaft 17 is supported at two separate bearings, it will not be possible to swing minutely in the angular direction.
[0045]
As described above, in the present embodiment, the bearing support of the high-speed side shaft 17 is limited to only one set of two angular ball bearings 24 and 25 that are frontally combined.
[0046]
On the wedge roller type transmission A side, as shown in FIG. 5, two angular ball bearings (24, 25) are combined in front, so that the angular rigidity of the high speed side shaft 17 can be reduced, and the high speed side shaft 17 It can swing slightly in the angular direction, and can absorb machining errors, assembly errors, and minute movements.
[0047]
The high-speed side shaft 17 is not only supported by the two angular ball bearings (24, 25), but also supported by rollers 37a, 37b, 38 on the wedge roller type transmission A side, and substantially two points. Supported by. Therefore, the high-speed side shaft 17 is firmly supported on the high-speed rotating machine X side without causing a problem such as miso motion.
[0048]
Therefore, according to the present invention, the demands of the wedge roller type transmission A and the demands of the high-speed rotating machine X, which have conventionally been incompatible, can be satisfied. Machine) can be provided.
[0049]
FIG. 9 is a cross-sectional view of an example in which a wedge roller type transmission A is used as a speed increase gear and a normal pulley P is mounted on the low-speed side shaft 3. As in this example, the wedge roller type transmission A is used as a speed increaser of a high-speed rotating machine. The wedge roller type transmission A is a traction drive, and can perform quiet and smooth power transmission even at high speed rotation. Therefore, there is no problem of vibration and noise. Further, the pressing force required for the traction drive is a mechanism obtained by a wedge action, and an appropriate pressing force proportional to the transmission torque is always obtained, so that no slip occurs. At the same time, high efficiency is obtained from the low rotation and low torque region to the high rotation and high torque region.
[0050]
However, the wedge roller type transmission A has a one-way power transmission type and a two-way power transmission type, and can be applied to both. In the case of the one-way power transmission type, there is a one-way clutch function. Since the pulley P is used, there is a drag torque due to the pressurized spring even during idling, and there is a possibility that the rotation fluctuation of the engine cannot be completely removed.
[0051]
Therefore, in the present embodiment, as shown in FIG. 1, a pulley P having a one-way clutch Y is used on the low-speed shaft 3 (input side) of the wedge roller type transmission A. The pulley P is spline-fitted to the end of the low-speed side shaft 3 and is fixed by a nut 50.
[0052]
Therefore, the rotation fluctuation from the engine is reduced and input to the wedge roller type transmission A, so that the rotation fluctuation in the transmission A is reduced, torsional vibration applied to the high-speed rotation machine is suppressed, and the high-speed rotation machine is controlled. Can be prevented from becoming insufficient in strength.
[0053]
Next, the pulley P incorporating the one-way clutch Y will be described with reference to FIG. FIG. 6 is a sectional view of a pulley incorporating a one-way clutch.
[0054]
A driven pulley 207a is arranged around the sleeve 208 concentrically with the sleeve 208. A pair of support bearings 209 and 209 and a roller clutch 210 (one-way clutch Y), which is a one-way clutch, are provided between the outer peripheral surface of the sleeve 208 and the inner peripheral surface of the driven pulley 207a.
[0055]
At the center of the outer peripheral surface of the sleeve 208, a convex portion 213 projecting diametrically outward from the outer peripheral surface is formed over the entire circumference. The outer peripheral surface of the driven pulley 207a has a wavy cross-sectional shape in the width direction, and a part of an endless belt called a poly-V belt can be freely passed over. The inner peripheral surface of the driven pulley 207a is a simple cylindrical surface. A roller clutch 210 (one-way clutch Y) is provided at an axially intermediate portion of a space existing between the outer peripheral surface of the sleeve 208 and the inner peripheral surface of the driven pulley 207a. Support bearings 209 and 209 are arranged at positions sandwiching the clutch 210 from both sides in the axial direction.
[0056]
The roller clutch 210 allows the transmission of rotational force between the driven pulley 207a and the sleeve 208 only when the driven pulley 207a tends to rotate relative to the sleeve 208 in a predetermined direction. In order to constitute such a roller clutch 210, an inner ring 214 for a roller clutch is externally fitted and fixed to a convex portion 213 formed on the outer peripheral surface of the sleeve 208 by interference fit. The roller clutch inner ring 214 is formed into a cylindrical shape as a whole by subjecting a steel plate such as carburized steel to plastic working such as press working, and has a cam surface 215 formed on an outer peripheral surface. That is, a plurality of concave portions 216 called ramps are formed on the outer peripheral surface of the inner ring 214 for the roller clutch at equal intervals in the circumferential direction, so that the outer peripheral surface is the cam surface 215.
[0057]
On the other hand, in the inner peripheral surface of the outer ring 217 for the roller clutch fixed to the inner peripheral surface of the intermediate portion of the driven pulley 207a by interference fit, at least the axial intermediate portion that comes into contact with the roller 219 described below is a simple cylinder. And the surface. The outer ring 217 for such a roller clutch is also formed by subjecting a steel plate such as carburized steel or the like to plastic working such as press working so as to be entirely formed in a cylindrical shape. Is formed. One of the flange portions 218a and 218b (left side in FIG. 6) is formed in advance at the time of manufacturing the outer ring 217 for the roller clutch. It has the same thickness. On the other hand, the other (rightward in FIG. 6) flange portion 218b is formed by incorporating a roller 219 and a clutch retainer 220 described below inside the diametrically inner side of the roller clutch outer ring 217. It is thin.
[0058]
A plurality of rollers 219 constituting the roller clutch 210 together with the inner ring 214 for the roller clutch and the outer ring 217 for the roller clutch are made of a synthetic resin which is externally fitted to the inner ring 214 for the roller clutch so as to be unable to rotate with respect to the inner ring 214 for the roller clutch. Roller and a slight displacement in the circumferential direction are supported by a clutch retainer 220 made of the same. A spring such as a leaf spring or a synthetic resin spring integrated with the clutch retainer 220 is provided between the pillar provided on the clutch retainer 220 and each roller 219. Are elastically pressed in the same direction with respect to the circumferential direction. Further, in the state shown in the figure, both axial end surfaces of the clutch retainer 220 are closely opposed to the inner side surfaces of both flange portions 218a and 218b constituting the outer ring 217 for the roller clutch, and the clutch retainer 220 is It prevents displacement in the direction. Since the basic structure and operation of such a roller clutch 210 are well known in the art, further detailed illustration and description will be omitted.
[0059]
The support bearings 209 and 209 allow the driven pulley 207a and the sleeve 208 to rotate relative to each other while supporting the radial load applied to the driven pulley 207a. In the case of this example, a deep groove ball bearing is used as each of the support bearings 209 and 209. That is, each of these support bearings 209, 209 has a bearing outer ring 222, 222 having a deep groove type outer raceway 221, 221 on the inner peripheral surface, and a bearing having a deep groove type inner raceway 223, 223 on the outer peripheral surface. The inner races 224 and 224 and the balls 225 and 225, which are rolling elements, are provided between the outer raceways 221 and 221 and the inner raceways 223 and 223, respectively. Further, by attaching seal rings 227, 227 to locking grooves 226, 226 formed on the inner peripheral surfaces of both ends of the bearing outer rings 222, 222, both ends of the spaces 228, 228 in which the balls 225, 225 are installed. The opening is closed.
[0060]
(2nd Embodiment)
Next, a second embodiment will be described. FIG. 7 is a cross-sectional view of a wedge roller type transmission according to a second embodiment of the present invention. FIG. 8 is a sectional view of a pulley incorporating a torsional damper.
[0061]
In the present embodiment, a pulley P containing a torsion damper Z is used instead of a pulley P containing a one-way clutch Y. The pulley P is spline-fitted to the end of the low-speed side shaft 3 and is fixed by a nut 50.
[0062]
Therefore, the rotation fluctuation from the engine is reduced and input to the wedge roller type transmission A, so that the rotation fluctuation in the transmission A is reduced, torsional vibration applied to the high-speed rotation machine is suppressed, and the high-speed rotation machine is controlled. Can be prevented from becoming insufficient in strength.
[0063]
Next, a pulley P having a built-in torsional damper Z will be described with reference to FIG. FIG. 8 is a sectional view of a pulley incorporating a torsional damper.
[0064]
The hub 301 integrally includes a mounting portion 301a for a shaft (not shown), a rising portion 301b extending radially outward, and a rim-shaped cylindrical portion 301c. , An elastic body 303 and a mass body (also referred to as a vibration ring) 304 are provided. A mounting sleeve 305 is fitted on the outer peripheral side of the mounting portion 301a, and a pulley 307 is connected to the outer peripheral side of the mounting sleeve 305 via a coupling rubber 306. The pulley 307 is connected to the inner peripheral side of the cylindrical portion 301c. Are integrally provided with a cylindrical portion 307a, a flange portion 307b, and a pulley groove portion 307c arranged on the outer peripheral side of the mass body 304. The pulley groove 307c is formed in a poly-V shape in which small V grooves are arranged in a plurality of axial directions. A bearing 308 is interposed between the mass 304 and the pulley groove 307c, and a thrust bearing 308a interposed between the mass 304 and the flange 307b is integrally formed with the bearing 308. At the axial end (right end in the drawing) 307d of the cylindrical portion 307a on the side opposite to the flange 307b, a part of the projection 307e on the circumference is provided toward one axial direction (right in the drawing). The protrusion 307e is inserted into an arc-shaped hole 301d provided in the rising portion 301b, and the combination of the protrusion 307e and the hole 301d engages in the circumferential direction to rotate the hub 301 and the pulley 307 relative to each other. Is limited to a predetermined angle.
[0065]
The hub 301 is formed in a ring shape from a predetermined metal. The hole portion 301d may not be penetrated in the axial direction as long as the protrusion 307e can be relatively rotated and can be engaged in a circumferential direction at a predetermined angle. The elastic body 303 is formed in a ring shape from a predetermined rubber-like elastic material, and is press-fitted between the cylindrical portion 301c and the mass body 304 from one side in the axial direction. The mass body 304 is formed in a ring shape from a predetermined metal. The mass body 304 has a step 304a on the outer peripheral surface, and has a small diameter portion 304b and a large diameter portion 304c with the step 304a as a boundary, and a pulley groove 307c is arranged on the outer peripheral side of the small diameter portion 304b. . The outer diameter of the large diameter portion 304c is set to be larger than the outer diameter of the pulley groove 307c. The torsion damper part 302 including the elastic body 303 and the mass body 304 is a fitting type torsion damper part in which the elastic body 303 is press-fitted between the cylindrical part 301c and the mass body 304. The elastic body 303 may be vulcanized and bonded between the mass body 304 and the mass body 304, and the mounting sleeve may be a bushing type torsion damper part which is fitted to the cylindrical part 301c. The mounting sleeve 305 and the pulley 307 are each formed in a ring shape from a predetermined sheet metal. The bearing 308 is formed in a ring shape from a predetermined resin, but its type or material is not particularly limited. The coupling rubber 306 is formed into an annular shape by a predetermined rubber-like elastic material, and is simultaneously vulcanized and bonded to each of the mounting sleeve 305 and the pulley 307 at the same time as the molding.
[0066]
The coupling rubber 306 is incorporated in the damper so that the axial relative positions of the inner peripheral end 306a and the outer peripheral end 306b are different from those at the time of molding. Has been granted. That is, when the coupling 306 is formed, the axial relative position of the mounting sleeve 305 with respect to the pulley 307 is set to the position shown by the chain line in the drawing, and the mounting sleeve 305 and the pulley 307 are shifted in the axial direction. Then, the coupling rubber 306 is molded and vulcanized and bonded to each of the mounting sleeve 305 and the pulley 307. As a result, the coupling rubber 306 is formed into a shape indicated by a chain line in the figure, and this shape is formed as an original shape (original shape). When a rubber-like elastic material (coupling rubber 306) is formed and bonded so as to be bridged between two rigid materials (the mounting sleeve 305 and the pulley 307), the rubber is used as long as the relative positions of the two rigid materials do not change. The rubber-like elastic material thermally shrinks after molding and is pulled between the two rigid materials, and if used in this state, the load is large and the rubber-like elastic material is deteriorated early. . In order to prevent this, it is only necessary to apply a pre-compression to the rubber-like elastic material after molding and change the tension state to the compression state. Therefore, in the damper, the coupling rubber 306 molded in a broken line shape is used. In order to adhere to the damper in the state of the solid line, the coupling rubber 306 is incorporated into the damper such that the axial relative positions of the inner peripheral end 306a and the outer peripheral end 306b are different from those at the time of molding. As a result, the distance between the inner peripheral end 306a and the outer peripheral end 306b is shortened at a large ratio, so that a large pre-compression is applied to the coupling rubber 306. The mounting sleeve 305 is press-fitted until it comes into contact with an engaging step portion 301e provided on the outer peripheral surface of the mounting portion 301a. When the mounting sleeve 305 is press-fitted to this point, the pulley 7 is pressed against the mass body 304 via the thrust bearing 308a by the elasticity of the coupling rubber 306. That is, the thrust bearing portion 308a maintains the state of the relative position being changed, and the pulley 307 is constantly pressed against the mass body 304 via the thrust bearing portion 308a.
[0067]
The damper having the above configuration is attached to the end of the low-speed side shaft 3 with the attachment portion 301a, and is transmitted from the crankshaft when torque is transmitted by winding an endless belt (not shown) around the pulley groove 307c. Torque fluctuations can be absorbed.
[0068]
The present invention is not limited to the above-described embodiment, but can be variously modified.
[0069]
【The invention's effect】
As described above, according to the present invention, a friction roller type transmission utilizing a wedge action is used as a speed increasing device of a high-speed rotating machine, and the wedge roller type transmission is a traction drive, Since the power can be transmitted quietly and smoothly, there is no problem of vibration or noise. Further, the pressing force required for the traction drive is a mechanism obtained by a wedge action, and an appropriate pressing force proportional to the transmission torque is always obtained, so that no slip occurs. At the same time, high efficiency is obtained from the low rotation and low torque region to the high rotation and high torque region.
[0070]
Further, the low-speed side shaft includes a pulley via a one-way clutch, or includes a pulley via a torsional damper.
[0071]
Therefore, the rotational fluctuation from the engine is reduced and input to the wedge roller type transmission, so that the rotational fluctuation in the transmission is reduced, torsional vibration applied to the high-speed rotating machine is suppressed, and the output of the high-speed rotating machine is reduced. It is possible to eliminate the possibility that the shaft has insufficient strength. Note that a diesel engine is particularly effective because the engine rotation fluctuation is large.
[Brief description of the drawings]
FIG. 1 is a sectional view showing an internal structure of a wedge roller type transmission according to a first embodiment of the present invention.
FIG. 2 is a sectional view taken along the line bb in FIG. 1;
FIG. 3 is a diagram illustrating the operation of a wedge roller type transmission.
FIG. 4 is a cross-sectional view of a wedge roller type transmission capable of transmitting torque when rotating in both forward and reverse directions according to the present invention.
FIG. 5 is an enlarged cross-sectional view of an example in which two angular ball bearings are combined in front;
FIG. 6 is a sectional view of a pulley incorporating a one-way clutch.
FIG. 7 is a sectional view of a wedge roller type transmission according to a second embodiment of the present invention.
FIG. 8 is a sectional view of a pulley incorporating a torsional damper.
FIG. 9 is a cross-sectional view of an example in which a wedge roller type transmission is used as a gearbox and a normal pulley is mounted on a low-speed side shaft.
[Explanation of symbols]
1, 101 housing
2,102 housing (partition plate)
3,103 Low speed shaft
4 Disc-shaped members
14 Connecting plate
17, 117 High speed side shaft
22 Thrust needle bearing
23,123 holes
24, 25 angular contact ball bearing
26 Preload member
27 Projection
28 volts
29 Sealing member
30 Double row angular contact ball bearing
31, 131a, 131b Deep groove ball bearing
32 Outer ring (low-speed side shaft)
33 Retaining ring
34 volts
36 Annular space
37, 37a, 37b Guide roller
38, 38a, 38b Movable roller
39a, 39b Support shaft
40 mating hole
41, 41a support holes
42 Radial needle bearing
43 Cylindrical surface for power transmission
44 Driven cylindrical surface
45 Drive side cylindrical surface
46 Cylinder hole
47 Elastic material
48 Inside contact part
49 Outer diameter side contact part
50 nuts
207a
A Wedge roller type transmission (speed increaser)
P pulley
X High-speed rotating machine
Y one way clutch
Z Torsional damper
207a driven pulley
208 sleeve
209 Support bearing
210 roller clutch
213 convex
214 Inner ring for roller clutch
215 Cam surface
216 recess
217 Outer ring for roller clutch
218a, 218b collar
219 Laura
220 clutch retainer
221 Outer ring track
222 Outer ring for bearing
223 Inner ring track
224 Inner ring for bearing
225 balls
226 Lock groove
228 space
301 hub
301a mounting part
301b rising part
301c cylindrical part
301d hole
301e engaging step
302 Torsional damper
303 elastic
304 mass
304a step
304b small diameter part
304c Large diameter part
305 Mounting sleeve
306 coupling rubber
306a Inner circumference end
306b Outer edge
307 pulley
307a cylindrical part
307b Flange part
307c Pulley groove
307d axial end
307e protrusion
308 bearing
308a Thrust bearing
309 Stopper

Claims (3)

The low-speed side shaft is rotatably supported on the housing, and an outer ring is provided at one end of the low-speed side shaft, while the eccentricity is provided with respect to the low-speed side shaft and the outer ring, and the high-speed side shaft is rotatably supported,
At least one guide roller and at least one movable roller that moves during torque transmission between the outer ring and the high-speed side shaft,
The low-speed side shaft is provided with a pulley via a one-way clutch. The low-speed side shaft is rotatably supported on the housing, and an outer ring is provided at one end of the low-speed side shaft, while the eccentricity is provided with respect to the low-speed side shaft and the outer ring, and the high-speed side shaft is rotatably supported,
At least one guide roller and at least one movable roller that moves during torque transmission between the outer ring and the high-speed side shaft,
The low-speed side shaft is provided with a pulley via a torsional damper. 3. The friction roller type transmission utilizing a wedge action according to claim 1, wherein the pulley is driven.

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