JP2015218804A - Transmission device utilizing planetary gear mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact transmission device configured by combining two planetary gear mechanisms, reduced in change of rotating speeds between an input shaft and an output shaft, and capable of easily obtaining rotary output in a reverse direction.SOLUTION: A first planetary gear mechanism is configured by disposing a first planetary gear PG1 journaled to a carrier 4A between a first ring gear RG1 fixed to an input shaft of a transmission device and a first sun gear SG1 fixed to an output shaft 3 of the transmission device. The carrier 4A is combined to rotate integrally with a cup-shaped carrier 4A, and a second planetary gear PG2 journaled to a carrier 4B configures a second planetary gear mechanism with a second ring gear RG2 fixed to a housing 1 and a second sun gear SG2 fixed to the input shaft 2. In the transmission device, by properly setting the number of teeth of each gear, the output shaft 3 can be rotated in a reverse direction at a rotating speed closer to a rotating speed of the input shaft 2, and the input in the reverse direction from the output shaft can be easily cut off.

Description

  The present invention relates to a transmission that changes a power transmission state between an input shaft and an output shaft, and in particular, transmission that performs a shift using a planetary gear mechanism in which a planetary gear is disposed between a sun gear and a ring gear. It relates to the device.

  In a power transmission system that rotationally drives mechanical parts, work equipment, or the like, an increase / decrease device for changing the rotational speed or torque is conventionally used to match the characteristics of the driven equipment. In OA equipment such as a copying machine, various devices are driven by using a very small motor as a drive source. However, since a small motor has high speed rotation and low torque, the rotation speed is adjusted at that time. A small speed reducer is often interposed in the power transmission system. In order to enable rotation in the reverse direction using a motor that rotates only in one direction as a drive source, a reversible transmission may be interposed.

  Further, in a lifting device that moves an article up and down by a motor, when the article reaches a predetermined position, an operation may be required in which the article automatically holds the position when the motor is stopped. In order to perform such an operation, the transmission device that transmits normal / reverse rotation power from the input shaft (motor side) and the power transmission from the output shaft (up-and-down article side) Yes, it is called a lock-type bidirectional clutch. With the lock-type bidirectional clutch, when the motor is stopped, the article can be prevented from falling without applying an operation such as an electric brake, leading to energy saving. Such a lock type bidirectional clutch is disclosed in, for example, Japanese Patent No. 4850653.

  By the way, among the speed reducers, there is a planetary gear type using a planetary gear mechanism. The planetary gear mechanism has a sun gear (sun gear) at the center and a ring gear (ring gear) that is an internal gear around the sun gear, and a plurality of planetary gears that mesh with both gears between the sun gear and the ring gear. A gear (planetary gear) is arranged, and a plurality of planetary gears are attached to and supported by a carrier (also called a retainer) that carries the planetary gear. The planetary gear type speed reducer has features that each gear and carrier can be freely selected as input / output elements, and the input shaft and output shaft are concentrically arranged, so that the layout design of the power transmission device is easy. is there.

As a speed reducer using a planetary gear mechanism, a speed reducer combining two planetary gear mechanisms each having a fixed ring gear and a rotating ring gear (hereinafter referred to as “differential planetary gear speed reducer”) is known. ing.
In the differential planetary gear reducer, as shown in FIG. 9, a plurality of planetary gears PG meshing with the sun gear SG fixed to the input shaft IS are arranged. As shown in the sectional view of FIG. 9A, the planetary gear PG is a gear that is relatively long in the axial direction, and meshes with both the fixed ring gear RGf and the rotating ring gear RGr arranged on the outer periphery thereof. The rotating ring gear RGr is fixed to the output shaft OS and can rotate, and a slight difference in the number of teeth is set between the number of teeth of both ring gears.

When the sun gear SG of the input shaft IS rotates, it rotates in the same direction as the sun gear SG based on the meshing of the planetary gear PG and the fixed ring gear RGf. The planetary gear PG is also meshed with the rotating ring gear RGr of the output shaft OS, and there is a slight difference in the number of teeth between both ring gears, so that the planetary gear PG revolves around the sun gear SG once (carrier CR ), The rotating ring gear RGr is rotated by the difference in the number of teeth. The gear ratio in the differential planetary gear reducer, that is, the ratio between the rotational speed nIS of the input shaft IS and the rotational speed nOS of the output shaft OS is expressed by the following equation.
nIS / nOS = (1+ (ZRGf / ZSG)) / (1- (ZRGf / ZRGr))
ZSG: Number of teeth of sun gear SG ZRGf: Number of teeth of fixed ring gear RGf ZRGr: Number of teeth of rotating ring gear RGr As is apparent from this equation, the gear ratio is small when the difference in the number of teeth of both ring gears is small. Thus, a reduction gear with a large reduction ratio and a corresponding increase in torque of the output shaft can be configured. Such a differential planetary gear reducer is disclosed in Japanese Patent Application Laid-Open No. 55-1000045 as an example.

Japanese Patent No. 4850653 JP-A-55-100455

In the above-described differential planetary gear speed reducer, a speed reducer with a very large speed ratio can be realized with a relatively simple structure. However, since the diameters of the fixed ring gear and the rotating ring gear are substantially the same and the difference in the number of teeth is small, it is difficult to configure a transmission device in which the rotational speed change between the input and output shafts is small. And the following problem arises on the relationship which meshes | combines the same planetary gear with respect to both the fixed ring gear and rotation ring gears from which the number of teeth differs.
If the pitch ring diameters of the fixed ring gear and the rotating ring gear are the same, the gear module value cannot be made the same because the number of teeth of the two gears is different. It is impossible to match the modules of both ring gears as they are. As a result, the degree of freedom of fixed ring gears, rotating ring gears, and the like that can be employed in the differential planetary gear reducer is limited, such as the need for a shift gear.
In addition, the teeth of the fixed ring gear and the rotating ring gear are arranged slightly shifted in the circumferential direction, and the phase difference of each tooth due to the shift indicates the difference in the number of teeth of both ring gears. The value is divided by the number of gear teeth. Therefore, when a common planetary gear is configured to mesh with both ring gears, the integer multiple of the number of planetary gears arranged in the circumferential direction is equal to the difference in the number of teeth of both ring gears. This causes a problem such as an increase in power transmission loss of the speed reducer and a deterioration in rotational balance.

  An object of the present invention is to configure a transmission device such as a speed reducer with low power transmission loss by combining two planetary gear mechanisms. In particular, there is little change in the rotational speed between input and output shafts and rotation in the reverse direction. It is to constitute a transmission device that can easily obtain an output. The transmission device of the present invention can be suitably used as a lock-type bidirectional clutch because the input shaft and the output shaft are concentric and the change in rotational speed between the input and output shafts can be set small.

In view of the above problems, the transmission device of the present invention configures the first planetary gear mechanism by arranging the first planetary gear between the ring gear fixed to the input shaft and the sun gear fixed to the output shaft. The rotational speed of the carrier of one planetary gear is determined by the carrier that supports the second planetary gear of the second planetary gear mechanism. That is, the present invention
“A transmission device having an input shaft and an output shaft that are installed opposite to the center of a fixed housing, and a first planetary gear mechanism and a second planetary gear mechanism that are installed in the housing in parallel in the axial direction. Because
The first planetary gear mechanism is interposed between a first ring gear fixed to the input shaft, a first sun gear fixed to the output shaft, and between the first ring gear and the first sun gear. A plurality of first planetary gears,
The second planetary gear mechanism includes a second ring gear fixed to the housing, a second sun gear fixed to the input shaft together with the first ring gear, and the second ring gear and the second sun gear. A plurality of second planetary gears interposed between the two,
The first planetary gear and the second planetary gear are supported on a common carrier.
It is a transmission device characterized by this.

According to a second aspect of the present invention, the carrier is provided with a cup-shaped member having a disk portion and a circumferential wall portion, and a disk-shaped member fitted to the cup-shaped member, and the first planetary gear mechanism. In the cup-shaped member of the carrier, and the second planetary gear mechanism can be disposed between the cup-shaped member of the carrier and the end surface on the input shaft side of the housing.
In this case, as described in claim 3, the first ring gear is formed on a peripheral wall provided around the disc, and the disc of the first ring gear is the cup-shaped member of the carrier. It is preferable to be configured so as to be in contact with the disc portion and to be supported in the thrust direction. According to a fourth aspect of the present invention, an end surface perpendicular to the axial direction is formed inside the housing, and a disc-shaped lid is fitted into an end facing the end surface. It is preferable that both surfaces are in contact with the end surface and the lid body and are supported in the thrust direction.

By the way, in claim 1, the second ring gear of the second planetary gear mechanism is fixed to the housing, and the rotation speed of the carrier of the first planetary gear mechanism (common with the carrier of the second planetary gear mechanism) is determined. However, the second sun gear of the second planetary gear mechanism can be fixed to the housing to determine the rotation speed of the carrier. At this time, as described in claim 5,
“A transmission device having an input shaft and an output shaft that are installed opposite to the center of a fixed housing, and a first planetary gear mechanism and a second planetary gear mechanism that are installed in the housing in parallel in the axial direction. Because
The first planetary gear mechanism is interposed between a first ring gear fixed to the input shaft, a first sun gear fixed to the output shaft, and between the first ring gear and the first sun gear. A plurality of first planetary gears,
The second planetary gear mechanism includes a second sun gear fixed to the housing, a second ring gear fixed to the input shaft together with the first ring gear, and the second ring gear and the second sun gear. A plurality of second planetary gears interposed between the two,
The first planetary gear and the second planetary gear are supported on a common carrier.
It becomes a transmission device characterized by this.

  According to a fifth aspect of the present invention, as in the sixth aspect, the second ring gear is preferably formed on the inner periphery of a ring-shaped member fitted to the first ring gear.

The transmission device according to claim 1 of the present invention includes an input shaft and an output shaft that are installed to face the center of a fixed housing, a first planetary gear mechanism that is installed in the housing in parallel in the axial direction, and a first planetary gear mechanism. 2 planetary gear mechanisms, and the input shaft of the transmission device is a ring gear (first ring gear) of the first planetary gear mechanism, and the output shaft is a sun gear (first sun gear) of the first planetary gear mechanism. Each is fixed. A plurality of planetary gears (first planetary gears) of the first planetary gear mechanism are rotatably supported by a carrier, and this carrier supports a planetary gear (second planetary gear) of the second planetary gear mechanism. It is common with careers. In the second planetary gear mechanism, the ring gear (second ring gear) is fixed to the housing and cannot rotate, and the sun gear (second sun gear) is connected to the first planetary gear on the input shaft of the transmission. It is fixed together with the ring gear (first ring gear) of the mechanism.
In the transmission device of the present invention, the first planetary gear and the second planetary gear supported by the carrier are separate gears that can be rotated at different rotational speeds, and as the first planetary gear and the second planetary gear. It is possible to employ gears having different numbers of teeth and pitch circle diameters. Therefore, the sun gear, ring gear, and planetary gear modules constituting each planetary gear mechanism can be made the same so that the meshing state of each gear is smooth, and power transmission loss can be reduced.

In the transmission device according to the first aspect of the present invention, the transmission gear ratio, which is the ratio between the rotational speed of the input shaft and the rotational speed of the output shaft, can be calculated as follows.
In general, in a planetary gear mechanism, if the gear ratio between the number of teeth of the ring gear and the number of teeth of the sun gear is γ, the rotation speed between the sun gear rotation speed nSG, the ring gear rotation speed nRG, and the carrier rotation speed nCR There is the following relationship.
nRG + γ · nSG = (1 + γ) nCR
γ = ZSG / ZRG ZSG: number of teeth of sun gear, ZRG: number of teeth of ring gear The transmission gear ratio of the present invention is determined by the rotational speed nRG1 of the rotating ring gear and the rotational speed nSG1 of the sun gear in the first planetary gear mechanism. Since the carrier rotation speed nCR common to the first and second planetary gear mechanisms is determined by the second planetary gear mechanism having the non-rotatable ring gear RG2, the following equation is obtained. .
nSG1 / nRG1 = (γ2- (1 / γ1)) / (γ2 + 1): Formula <1>
γ1: Tooth ratio of the first planetary gear mechanism, γ2: Tooth ratio of the second planetary gear mechanism Here, since γ1 and γ2 are both smaller than 1, the numerator of the above formula is a negative value, and the present invention In this transmission device, the rotation direction of the output shaft is opposite to the rotation direction of the input shaft. The speed ratio can be freely set by changing γ1 and γ2, and the rotation direction can be easily reversed in a state where the change in the rotational speed is small (the absolute value of the speed ratio is close to 1). For example,
γ1 = 3/5, γ2 = 1/3
Then, the transmission device has the same rotation speed (constant speed) and the rotation direction is reversed. Also,
γ1 = 1/3, γ2 = 3/5
In this case, a transmission device can be configured in which the rotational speed is 3/2 and the rotational direction is reversed.

  Thus, in the transmission device of the present invention, the rotation center axes of the input shaft and the output shaft are concentric, and the rotation direction is reversed. In a normal reversing device in which a reverse gear is provided on the output shaft, the input shaft and the output shaft are displaced. However, the transmission device of the present invention is concentric, and is small and compact, so that power transmission Convenience in the system is excellent. For example, the transmission device of the present invention can be suitably used when an inexpensive motor capable of only rotating in one direction is used as a drive source to obtain a rotational output in the reverse direction. Further, in the transmission device of the present invention, when driven from the output shaft side, it becomes locked and power transmission to the input shaft becomes impossible, so that it can be used as a lock type bidirectional clutch.

  The invention of claim 2 relates to a carrier that pivotally supports the planetary gears of the first planetary gear mechanism and the second planetary gear mechanism, and the carrier is assembled with a cup-shaped member and a disk-shaped member fitted thereto. Structure. The first planetary gear mechanism is disposed inside the cup-shaped member of the carrier, and the second planetary gear mechanism is disposed between the cup-shaped member and the end surface on the input shaft side of the housing. As a result, the first planetary gear mechanism is arranged inside the cup-shaped member of the carrier, and the second planetary gear mechanism is installed in parallel in the axial direction, so that the structure of the entire transmission device is made compact.

  According to a third aspect of the present invention, the first ring gear in the first planetary gear mechanism is formed on a peripheral wall provided around the disk, and the disk of the first ring gear is used as the cup-shaped member of the carrier of the second aspect. Bearing in the thrust direction by abutting against the disc portion. As a result, the input shaft to which the first ring gear is fixed is prevented from tilting or vibrating during rotation, and stable rotation of the transmission is achieved. Further, as in the invention of claim 4, a disc-shaped lid is fitted into the end portion of the housing, and both end surfaces in the axial direction of the carrier are brought into contact with the vertical end surface of the housing and the lid body in the thrust direction. In the case of bearings, not only the first ring gear of the input shaft and the sun gear of the output shaft, but also the carrier itself is supported in the thrust direction, and the entire rotating body of the transmission device rotates stably.

According to a fifth aspect of the present invention, the first planetary gear mechanism includes a first ring gear fixed to the input shaft, a first sun gear fixed to the output shaft, and a planetary gear supported by the carrier. However, in the second planetary gear mechanism that determines the rotation speed of the carrier, the sun gear (second sun gear) is fixed to the housing in a non-rotatable manner. In the transmission device according to the fifth aspect having this configuration, the gear ratio is as follows.
nSG1 / nRG1 = (1- (γ2 / γ1)) / (γ2 + 1): Formula <2>
γ1: Tooth ratio of the first planetary gear mechanism, γ2: Tooth ratio of the second planetary gear mechanism As can be seen from the above equation, in the transmission device according to the fifth aspect of the present invention, the output shaft is positive or negative depending on the magnitude of γ1 and γ2. The rotation / reversal is determined, and if γ2> γ1, the rotation is reversed. For example,
γ1 = 1/5, γ2 = 1/2
Then, the transmission device has the same rotation speed and reverse rotation direction.

  In the transmission device according to claim 5, when the output shaft is reversely rotated, it is necessary to make the gear ratio of the second planetary gear mechanism larger than that of the first planetary gear mechanism. Therefore, the ring gear (second gear of the second planetary gear mechanism). It is desirable to make the diameter of the ring gear smaller than that of the first planetary gear mechanism. When the second ring gear is formed on the inner periphery of the ring-shaped member fitted to the ring gear (first ring gear) of the first planetary gear mechanism as in the invention of claim 6, the transmission device of claim 5 The overall structure can be simplified, and the manufacturing and assembly can be facilitated.

It is a figure which shows the whole structure of 1st Example of the transmission of this invention. It is a figure which shows stationary components, such as a housing, in the transmission of FIG. It is a figure which shows the input / output member in the transmission of FIG. It is a figure which shows the planetary gear and the carrier in the transmission of FIG. It is a figure which shows the whole structure of 2nd Example of the transmission device of this invention. It is a figure which shows stationary components, such as a housing, in the transmission of FIG. It is a figure which shows the input-output member in the transmission of FIG. It is a figure which shows the planetary gear and carrier in the transmission of FIG. It is a figure which shows the structure of the conventional differential type planetary gear reducer.

The transmission device of the present invention will be described below with reference to the drawings. First, FIG. 1 shows the overall structure of a first embodiment of the transmission device according to the present invention (corresponding to the invention of claim 1), and FIGS. 2 to 4 show the components constituting the transmission device alone. .
As shown in the longitudinal sectional view in the center of FIG. 1, the transmission device of the first embodiment includes a first planetary gear mechanism (cross section AA) disposed on the left side in a fixed housing 1, and a right side. And a second planetary gear mechanism (cross section BB) arranged in parallel. At the center of the housing 1, an input shaft 2 (having a hatched cross section) and an output shaft 3 are installed facing each other, and the rotation centers of both shafts are concentric. The input shaft 2 is supported by a central hole at one end of the housing 1, and the output shaft 3 passes through a lid 1 </ b> C fitted to the other end of the housing 1 for shielding and is supported by this.

  The input shaft 2 is attached with a disk having a peripheral wall at the end on the output shaft 3 side, and the first ring gear RG1 of the first planetary gear mechanism is fixed to the peripheral wall (also in FIG. 3). reference). Further, the first sun gear SG1 of the first planetary gear mechanism is fixed to the output shaft 3 at the axial end of the input shaft 2 side. As shown in the section AA, in the first planetary gear mechanism, three first planetary gears PG1 are arranged around the first sun gear SG1, and the first planetary gear PG1 is connected to the first sun gear SG1. It meshes with the first ring gear RG1 of the input shaft 2. The first planetary gear PG1 is rotatably supported by a carrier 4A that is a disk-shaped member. Each gear is a cycloid gear having a tooth profile curve based on cycloid.

A second sun gear SG2 of the second planetary gear mechanism is also fixed to the input shaft 2 on the opposite side of the ring gear RG1 across the disc. The second ring gear RG2 of the second planetary gear mechanism is fixed to the inner surface of the housing 1 at this portion. As shown in the section BB, in the second planetary gear mechanism, three second planetary gears PG2 are arranged around the second sun gear SG2.
The second sun gear SG2 is rotatably supported on the carrier 4B. The carrier 4B is a cup-shaped member having a disk portion and a circumferential wall portion, and the second sun gear SG2 is fitted on a shaft standing on the back side of the cup-shaped member (see also FIG. 4). The circumferential wall portion of the carrier 4B surrounds the circumferential wall of the input shaft 2 to which the first ring gear RG1 is fixed, and the carrier of a disk-like member that pivotally supports the first planetary gear PG1 at the tip in the axial direction. 4A is fitted. That is, the carrier 4A of the first planetary gear mechanism and the carrier 4B of the first planetary gear mechanism constitute a carrier 4 that rotates integrally, and the first planetary gear mechanism is housed inside the carrier 4. Yes.

  In the transmission device of the present invention, the first planetary gear PG1 and the second planetary gear PG2 supported by the carrier 4 are separate gears, and gears having different numbers of teeth and pitch circle diameters can be employed. Therefore, the sun gear, ring gear, and planetary gear modules constituting each planetary gear mechanism can be made the same so that the meshing state of each gear can be made smooth.

Next, a usage mode of the transmission device according to the first embodiment of the present invention will be described.
When this transmission device is used in a power transmission system, a motor or the like as a drive source is connected to the input shaft 2, and a driven device or the like is connected to the output shaft 3. The central hole of the input shaft 2 and the output shaft 3 are each formed with a flat portion for preventing rotation with a connecting shaft (not shown). When the input shaft 2 is rotated by a motor or the like, the carrier 4 is decelerated by the second planetary gear mechanism including the second sun gear SG2 of the input shaft 2 and the non-rotatable second ring gear RG2 fixed to the housing 1. Rotate. In the first planetary gear mechanism, the rotational speed of the first sun gear SG1 fixed to the output shaft 3 is determined by the rotational speed of the first ring gear RG1 of the input shaft 2 and the rotational speed of the carrier 4, and the output shaft 3 and the input The transmission ratio that is the rotation speed ratio with the shaft 2 is expressed by the formula <1>.
In the first embodiment, the number of teeth of each gear constituting the planetary gear mechanism includes the first ring gear RG1: 45, the first sun gear SG1: 27 (γ1 = 3/5), and the second ring gear RG2. : 45, second sun gear SG2: 15 (γ2 = 1/3). Therefore, the gear ratio is −1, and the transmission device of the first embodiment operates as a reversing device whose rotational speed is the same (constant speed) and whose rotational direction is reversed. Although not shown, if the number of teeth of the first and second planetary gear mechanisms of the first embodiment is changed and γ1 = 1/3 and γ2 = 3/5 are set, the rotation speed is 3/2 and the rotation direction is reversed. A transmission device can be obtained.

  In the transmission device of the first embodiment, the rotation shafts of the input shaft 2 and the output shaft 3 are concentric and the rotation direction is reversed, and the gear ratio is determined by the gear teeth of the planetary gear mechanism. It can be set freely by changing the number. Further, when driving from the input shaft 2 side, the first planetary gear PG1 and the second planetary gear PG2 are simultaneously rotated by the input shaft 2, but conversely when driving from the input shaft 2 side, first the first planetary gear PG2 is driven. Since the driving force is transmitted only to PG1, power transmission to the input shaft 2 becomes difficult. For these reasons, the transmission of the first embodiment can be suitably used as a lock-type bidirectional clutch.

  2, the housing 1 is a cup-shaped fixing member that includes a circumferential wall 11 and an end plate 12, and an end face 13 that is perpendicular to the axial direction is formed inside the housing 1. A step portion to be formed is provided, and a second ring gear RG2 of the second planetary gear mechanism is provided in a portion having a small diameter. A lid 1C is fitted into the end of the housing 1 facing the end face 13, and the end plate 12 and the lid 1C of the housing 1 are provided with central holes through which the input shaft 2 and the output shaft 3 respectively penetrate. It is done. Further, as shown in the longitudinal sectional view in the center of FIG. 1, the carrier 4 is axially positioned with both axial end faces coming into contact with the end face 13 of the housing 1 and the lid 1 </ b> C in the thrust direction. Has been done.

As shown in the single view of the input / output component in FIG. 3, the input shaft 2 is provided with a disk 21 at the end on the output shaft 3 side, and a first end is disposed at the radially outer end of the disk 21. A peripheral wall 22 in which the ring gear RG1 is formed is provided. A second sun gear SG2 is fixed to the opposite side of the disc 21 from the first ring gear RG1.
A first sun gear SG1 is fixed to the output shaft 3, and the first sun gear SG1 has a disc 21 whose both ends in the axial direction are the input shaft 2 as shown in the longitudinal sectional view in the center of FIG. And a carrier 4A, which is a disk-shaped member, and is supported in the thrust direction in a form sandwiched between them. The end surface of the disk 21 of the input shaft 2 is in contact with the disk-shaped surface of the carrier 4B, and a thrust bearing is performed. As a result, the input shaft 2, the output shaft 3, and the carrier 4 that are rotating members of the transmission device are all supported by the housing 1 that is a fixed member, and a situation such as tilting or vibration during rotation is prevented. And a stable rotation of the transmission is achieved.

Next, a second embodiment (corresponding to the invention of claim 5) of the transmission device of the present invention will be described with reference to FIGS. FIG. 5 shows the overall structure of the transmission device according to the second embodiment, and FIGS. 6 to 8 show components constituting the transmission device alone.
As shown in the longitudinal sectional view in the center of FIG. 5, the transmission of the second embodiment includes a first planetary gear mechanism (cross section AA) disposed on the right side in a fixed housing 1 ′, and a left side. And a second planetary gear mechanism (cross-section BB) arranged in parallel to each other. At the center of the housing 1 ', an input shaft 2' (having a hatched cross section) and an output shaft 3 'are installed facing each other, and the rotation centers of both shafts are concentric. The input shaft 2 'is supported by a central hole at one end of the housing 1', and the output shaft 3 'passes through a lid 1'C fitted to the other end of the housing 1' for shielding. Bearing.

  As shown in FIG. 7, a disk 21 ′ having a peripheral wall 22 ′ is attached to the input shaft 2 ′, and the peripheral wall 22 ′ has a first ring gear of the first planetary gear mechanism. Ring gear RG1 is fixed. The first ring gear RG1 is a gear formed over the entire length in the axial direction of the peripheral wall 22 '. The ring-shaped member 2'R is fitted into the opposite end of the disc 21' so as to be integrated. Is installed. The ring-shaped member 2′R is formed with an outer tooth 2′RT that fits with the first ring gear RG1, like a projection of a spline shaft, on the outer periphery, and on the inner periphery, the ring gear of the second planetary gear mechanism. The second ring gear RG2 is formed and fixed. The first sun gear SG1 of the first planetary gear mechanism is fixed to the output shaft 3 ′.

  As shown in section AA of FIG. 5, in the first planetary gear mechanism in the second embodiment, three first planetary gears PG1 are arranged around the first sun gear SG1 of the output shaft 3 ′. The first planetary gear PG1 meshes with the first sun gear SG1 of the output shaft 3 ′ and the first ring gear RG1 fixed to the input shaft 2 ′. In this respect, the first planetary gear mechanism PG1 is the same as the first planetary gear mechanism of the first embodiment. There is no change. The first planetary gear PG1 is rotatably supported on a shaft erected on one side (input shaft 2 ′ side) of the carrier 4 ′ that is a disk-shaped member (see also FIG. 8).

  In the second planetary gear mechanism in the second embodiment, the second sun gear SG2 is a non-rotatable gear, and is fixed to a lid 1′C fitted in the housing 1 ′ (see also FIG. 6). ). As shown in the cross section BB of FIG. 5, three second planetary gears PG2 are arranged between the second ring gear RG2 and the second sun gear SG2 fixed to the input shaft 2 ', and the second planetary gears PG2 are arranged. The gear PG <b> 2 is rotatably supported on the opposite side of the first planetary gear PG <b> 1 in the carrier 4 ′ that is a disk-shaped member (see also FIG. 8).

That is, in the transmission device of the second embodiment of the present invention, in the second planetary gear mechanism that determines the rotation speed of the carrier, the transmission device of the first embodiment fixes the ring gear to the housing in a non-rotatable manner. This corresponds to a sun gear fixed so as not to rotate. In the first embodiment, the carrier 4 has a complicated structure in which a cup-shaped member and a disk-shaped member are combined. However, the carrier 4 'of the transmission device of the second embodiment is simply a disk-shaped member. The structure has been simplified.
The gear ratio in the transmission of the second embodiment is calculated by the above-described <Equation 2>, but the number of teeth of each gear constituting the planetary gear mechanism of the second embodiment is the first ring gear RG1: 60, 1 sun gear SG1: 12 (γ1 = 1/5), second ring gear RG2: 48, and second sun gear SG2: 24 (γ2 = 1/2). Therefore, the gear ratio is −1, and the transmission device of the second embodiment operates as a reversing device in which the rotation speed is the same and the rotation direction is reversed, as in the first embodiment.

  As shown in the single view of the input / output component in FIG. 7, the first ring gear RG1 is formed on the peripheral wall 22 ′ of the input shaft 2 ′ over the entire length in the axial direction. Since the ring-shaped member 2′R is attached, in the transmission device of the second embodiment, the manufacture of the input shaft 2 ′ and the assembly of the transmission device are facilitated. Further, as shown in the longitudinal sectional view in the center of FIG. 5, the disc 21 ′ of the input shaft 2 ′ contacts the inner surface of the housing 1 ′, and the output shaft 3 ′ contacts the disc 21 ′ and thrust direction. Bearings are being made. For this reason, it is possible to prevent a situation in which the rotating member is tilted or vibrated during rotation.

  As described in detail above, the transmission device of the present invention configures the first planetary gear mechanism by arranging the first planetary gear between the ring gear fixed to the input shaft and the sun gear fixed to the output shaft, The number of rotations of the carrier of the first planetary gear is determined by the carrier that supports the second planetary gear of the second planetary gear mechanism. In the above-described embodiment, the transmission gear ratio is set to −1, and it is operated as a reversing device in which the rotation speed is the same and the rotation direction is reversed. However, by adjusting the number of teeth of each gear, the rotation speed increases or Needless to say, it is possible to construct a transmission device that decreases. Also, instead of forming the gear directly on the input shaft, etc., the gear part is manufactured separately and assembled to the parts, and the involute tooth profile and other special shape tooth profile are adopted as the tooth profile curve of each gear. Obviously, various modifications are possible.

1, 1 'housing 1C, 1'C cover plate 2, 2' input shaft 3, 3 'output shaft 4, 4' carrier SG1, SG2 (first and second planetary gear mechanism) sun gear PG1, PG2 (first 1, planetary gears RG1, RG2 (of the first planetary gear mechanism) ring gears (of the first, second planetary gear mechanism)

Claims (6)

A transmission device having an input shaft and an output shaft installed opposite to the center of a fixed housing, and a first planetary gear mechanism and a second planetary gear mechanism installed in parallel in the axial direction in the housing. There,
The first planetary gear mechanism is interposed between a first ring gear fixed to the input shaft, a first sun gear fixed to the output shaft, and between the first ring gear and the first sun gear. A plurality of first planetary gears,
The second planetary gear mechanism includes a second ring gear fixed to the housing, a second sun gear fixed to the input shaft together with the first ring gear, and the second ring gear and the second sun gear. A plurality of second planetary gears interposed between the two,
The transmission apparatus, wherein the first planetary gear and the second planetary gear are pivotally supported by a common carrier. The carrier includes a cup-shaped member having a disk portion and a circumferential wall portion, and a disk-shaped member fitted to the cup-shaped member, and the first planetary gear mechanism is disposed inside the cup-shaped member of the carrier. The transmission apparatus according to claim 1, wherein the second planetary gear mechanism is disposed between the cup-shaped member of the carrier and an end surface of the housing on the input shaft side. The first ring gear is formed on a peripheral wall provided around the disc, and the disc of the first ring gear abuts on the disc portion of the cup-shaped member of the carrier and is supported in the thrust direction. The transmission device according to claim 2. An end surface perpendicular to the axial direction is formed inside the housing, and a disc-shaped lid is fitted to an end portion facing the end surface, and both sides of the carrier are the end surface and the carrier. The transmission device according to claim 2 or 3, wherein the transmission device is in contact with the lid body and is bearing in the thrust direction. A transmission device having an input shaft and an output shaft installed opposite to the center of a fixed housing, and a first planetary gear mechanism and a second planetary gear mechanism installed in parallel in the axial direction in the housing. There,
The first planetary gear mechanism is interposed between a first ring gear fixed to the input shaft, a first sun gear fixed to the output shaft, and between the first ring gear and the first sun gear. A plurality of first planetary gears,
The second planetary gear mechanism includes a second sun gear fixed to the housing, a second ring gear fixed to the input shaft together with the first ring gear, and the second ring gear and the second sun gear. A plurality of second planetary gears interposed between the two,
The transmission apparatus, wherein the first planetary gear and the second planetary gear are pivotally supported by a common carrier. The transmission device according to claim 5, wherein the second ring gear is formed on an inner periphery of a ring-shaped member fitted to the first ring gear.