JP4283579B2 - Power transmission device having reverse rotation prevention function - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a power transmission device having a reverse rotation prevention function.
[0002]
The reverse rotation prevention function in the power transmission device refers to the rotation of the output shaft even if a torque to rotate the output shaft of the power transmission device is applied from the load side (drive target device side). It is a function that maintains the stopped state.
[0003]
[Prior art]
In the field of driving elevators, shutters, conveyors, solar power generation devices, valves for opening and closing flow paths, OA equipment, etc., power transmission devices having a reverse rotation prevention function capable of maintaining the stopped state are widely used. ing.
[0004]
Among power transmission devices having a reverse rotation prevention function, many techniques using a device that mechanically blocks rotation of a rotating member using a reverse rotation prevention bolt, a clutch, or the like when stopped are proposed. However, the structure that mechanically prevents the rotating member from rotating using such a device is used when the device to be driven stops due to an unexpected accident such as a power failure. There is a problem that it cannot function.
[0005]
Therefore, various so-called self-locking functions, i.e., a structure in which the power transmission device itself has a reverse rotation preventing function have been proposed as solutions for solving such problems.
[0006]
For example, a conventionally known solar power generation device shown in FIG. 11 is one in which a worm gear set is applied to a power transmission device.
[0007]
This solar power generation device 1 includes a horizontally-long rectangular solar cell panel 2, a drive motor 4 and a reduction gear group 5 that rotationally drive the solar cell panel 2 via a pipe-shaped horizontal shaft 3, and these solar cell panels 2. And a horizontal support base 6 that supports the drive motor 4 and the reduction gear group 5 and the like, and a second drive motor 8 and a second reduction gear group 9 that rotationally drive the horizontal support base 6 via a support member 7. Yes.
[0008]
The reduction gear group 5 and the second reduction gear group 9 of the solar power generation device 1 both have worm gear sets WG1 and WG2, thereby rotating the solar cell panel 2 and the horizontal support base 6 forward and backward. It is possible and has a function to prevent reverse rotation.
[0009]
[Patent Document 1]
JP 2001-102613 A
[0010]
[Problems to be solved by the invention]
However, the worm gear sets WG1 and WG2 applied to the conventionally known photovoltaic power generation apparatus 1 have a property that they are difficult to rotate due to torque from the output side, but have a problem that the efficiency of the original power transmission is low. is there. Therefore, in the case of manual driving, a large force is required for the operation, and the operability is likely to deteriorate. In the case of motor driving, a large-capacity motor is required and power consumption increases, and it is difficult to efficiently use the electricity generated by the solar cell panel 2.
[0011]
Further, as a typical configuration having a self-locking function, there is one in which a one-way clutch is interposed on a power transmission path. However, in this configuration, since the original direction of power transmission is limited to one direction, it is necessary to perform forward and reverse rotation like the reduction gear group 5 and the second reduction gear group 9 of the solar power generation device 1. It cannot be used for certain power transmission devices.
[0012]
In general, the self-locking property with respect to the torque from the load side and the rotational smoothness (rotational efficiency) with respect to the torque from the normal drive source side such as a motor are in a relation, and it is difficult to achieve both. In order to obtain a practical self-locking property, the actual situation is that it is unavoidable to use a worm gear set having a considerably low rotational efficiency.
[0013]
The present invention has been made to solve such a problem, and provides a power transmission device capable of improving the rotational efficiency of the entire device while having a high self-locking function. Objective.
[0014]
[Means for Solving the Problems]
The present invention includes a speed reduction mechanism including an input shaft and an output shaft, and a reverse rotation prevention function provided with a function of preventing the output shaft from rotating reversely when a torque that reversely rotates the output shaft is applied from the load side. In the power transmission device having the above, as the speed reduction mechanism, the starting efficiency is 40% or more However, the deceleration mechanism alone does not exhibit the reverse rotation prevention function. Friction force that employs a speed reduction mechanism and that can always apply resistance due to friction to any rotating member on the power transmission path at any position on the power transmission path of the speed reduction mechanism during operation. For the first time by disposing the applying means and always applying a frictional force to the rotating member by the frictional force applying means in the stopped state. Above The above problem is solved by the function of preventing reverse rotation.
[0015]
In the present invention, the difference between the static friction and the dynamic friction, or the difference between the starting efficiency and the operating efficiency is more actively utilized in the configuration. That is, in the present invention, as the speed reduction mechanism of the power transmission device that is intended to have the reverse rotation prevention function, basically, one having an activation efficiency of 40% or more is employed. Here, the starting efficiency means that when a predetermined rotational torque is applied to the input shaft while the output shaft is stopped, a value (100%) obtained by multiplying the rotational torque by a reduction ratio is generated on the output shaft. This is equivalent to η when only η% can be taken out. In the same power transmission device, the value is reproducible.
[0016]
The start efficiency of 40% or more means that the operation efficiency is higher. The operating efficiency changes depending on the magnitude of the load at that time, the rotational speed, or the like, but does not become lower than the starting efficiency. That is, the operating efficiency of the power transmission device according to the present invention is at least 40% or more.
[0017]
In the present invention, a resistance caused by friction is applied to any rotating member on the power transmission path at any position on the power transmission path of the speed reduction mechanism. "Fractive force imparting means are positively arranged.
[0018]
In the present invention, the operating efficiency of the speed reduction mechanism of the power transmission device is high, and the starting efficiency is lowered by the friction applying means. Since the frictional force applied by the friction applying means is drastically reduced when the speed reduction mechanism starts to rotate, the power transmission device can be operated with its original high efficiency.
[0019]
That is, when the device to be driven is stopped, that is, when the operation is to be resumed from when the power transmission device is stopped, the maximum static friction inherent in the speed reduction mechanism is reduced to the friction. As long as the reverse torque greater than the value obtained by adding the maximum static friction applied by the force applying means is not applied from the load side, the power transmission device maintains the stopped state (self-locking function).
[0020]
On the other hand, once the power transmission device starts rotating, not only the rotational efficiency increases by the difference between the dynamic friction force inherent to the deceleration mechanism and the static friction force so far, but also the friction applying means. The rotational efficiency is increased by the difference between the dynamic friction force at the time and the static friction force until then, and the power transmission device is operated in a state where the original high rotational efficiency is utilized.
[0021]
Since the friction application by the friction application means is always performed, the self-lock function is automatically exhibited not only when the normal operation is stopped, but also when the apparatus is stopped due to an unexpected accident such as a power failure.
[0022]
Preferably, the speed reduction mechanism may be configured to include at least a speed reducing portion of a swinging intermeshing planetary gear structure including an external gear and an internal gear having a slight difference in the number of teeth. The swinging intermeshing planetary gear structure itself has the characteristics of relatively high operating efficiency and relatively low starting efficiency (still 70% or more). Therefore, it is optimal as a speed reduction mechanism according to the present invention. The “slight difference in the number of teeth” referred to here means a difference in the number of teeth from about 1 to 6.
[0023]
Further, the frictional force applying means may be arranged on the rotating member positioned on the upstream side of the speed reducing portion of the planetary gear structure. Thereby, since the rotation of the output shaft can be prevented with a small frictional force, the configuration of the friction applying means can be reduced in size and cost, and the reduction in efficiency during operation can be reduced.
[0024]
Furthermore, when the power transmission device includes a manual operation shaft that can manually rotate the output shaft, the frictional force applying means may be disposed with respect to the manual operation shaft. As a result, the present invention can be implemented with a slight improvement over the existing power transmission device.
[0025]
Furthermore, if the magnitude of the frictional resistance imparted to the rotating member by the frictional force imparting means can be adjusted and changed, the required self-locking property can be obtained depending on the specific application. Fine adjustments can be made at the site considering the balance with rotational smoothness.
[0026]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, examples of embodiments of the present invention will be described in detail with reference to the drawings.
[0027]
FIG. 1 is a sectional view showing a geared motor to which a power transmission device according to an example of the first embodiment of the present invention is applied, and FIG. 2 is a plan view thereof. FIG. 1 corresponds to a developed cross-sectional view taken along the line II of FIG.
[0028]
The geared motor 10 includes a motor 12 independent as a drive source, and a reduction gear (power transmission device) 14 having a parallel shaft gear reduction portion G1 and a swing reduction portion G2 having an intermeshing planetary gear structure. It is.
[0029]
The casing 16 of the speed reducer 14 includes a main body casing 18 and an end cover 20 disposed on the opening side (upper side in the drawing), and is integrated by a bolt 24. The motor 12 can be connected to the main body casing 18.
[0030]
A pinion 30 is directly formed on the motor shaft 13 of the motor 12, and the motor shaft 13 also serves as an input shaft of the speed reducer 14. A through hole 20A into which the pinion 30 is inserted is formed in the main body casing 18 so that the pinion 30 faces the casing 16 of the speed reducer 14 when the main body casing 18 and the casing 29 of the motor 12 are connected. It is configured.
[0031]
The parallel shaft gear reduction part G <b> 1 accommodated in the casing 16 of the speed reducer 14 includes an intermediate shaft 31. A first gear 32 and a second pinion 33 that mesh with the pinion 30 are integrally attached to the intermediate shaft 31. The second pinion 33 meshes with the second gear 34 that is integrally attached to the eccentric body 42 of the swing reduction part G2 of the intermeshing planetary gear structure. The pinion 30, the intermediate shaft 31, the first gear 32, the second pinion 33, and the second gear 34 constitute a power transmission path of the parallel shaft gear reduction part G1.
[0032]
On the other hand, the swing reduction part G2 of the intermeshing planetary gear structure includes a support shaft 38 that is coaxially integrated with the output shaft 56, and the eccentric body 42 that is incorporated in the support shaft 38 via a roller bearing 40. The external gear 46, which is mounted on the eccentric body 42 via a roller bearing 44 and can be eccentrically swung around the support shaft 38, is integrated with the body casing 18, and the external gear 46 is inscribed The internal gear 48 which meshes is mainly provided.
[0033]
The support shaft 38 is integrally manufactured coaxially with the output shaft 56, and is supported on the end cover 20 and the main body casing 18 by ball bearings 50 and 55 together with the output shaft 56.
[0034]
As shown in the cross-sectional view of the rocking speed reducing portion G2 in FIG. 3, trochoidal external teeth are formed on the outer periphery of the external gear 46, and the internal teeth of the internal gear 48 are formed in arc-shaped grooves. It is comprised by the pin 49 incorporated rotatably. The number of teeth of the external gear 46 is “43”, which is one less than the number of teeth “44” of the internal gear 48 (a slight difference in the number of teeth). An internal pin hole 47 is formed in the external gear 46, and an internal pin 72 covered with an internal roller 70 for promoting sliding is loosely fitted. The inner pin 72 is fixed in a cantilever manner to a flange body 58 that is press-fitted integrally with the output shaft 56.
[0035]
Here, the configuration of a frictional force applying mechanism (frictional force applying means) for applying a frictional force to the power transmission path of the speed reducer 14 will be described.
[0036]
In this embodiment, the frictional force imparting mechanism F1 is arranged with respect to the first gear 32 of the parallel shaft gear reduction part G1, as shown in FIG. The first gear 32 corresponds to a rotating member located on the upstream side of the swing reduction portion G2 of the swing intermeshing planetary gear structure in terms of position on the power transmission path.
[0037]
As shown in the enlarged sectional view of FIG. 4, the frictional force imparting mechanism F1 is integrally attached to a second intermediate shaft 76 disposed in parallel to the intermediate shaft 31, and the second intermediate shaft 76. A third pinion 77 meshing with the first gear 32; a bush 78 having a sliding portion 78S that frictionally slides with the second intermediate shaft 76; and a recess 78A formed on the outer periphery of the bush 78; A ball 80 for maintaining the bush 78 in a non-rotating state, and a spring for adjusting the magnitude of the frictional resistance applied to the first gear 32 by adjusting the urging force of the ball 80 against the bush 78. 81 and an adjustment body 82 that accommodates the ball 80 and the spring 81.
[0038]
The second intermediate shaft 76 is rotatably supported by the end cover 20 and the main body casing 18 via a pair of bearings 83 and 84 having an L-shaped cross section. The sliding resistance between the bush 78 and the second intermediate shaft 76 (friction force at the sliding portion 78S) can be changed by adjusting the biasing force of the spring 81 against the ball 80. The biasing force by the spring 81 is adjusted by adjusting the relative position of the adjusting body 82 with respect to the bush 78.
[0039]
That is, a male screw 85 is formed on the outer periphery of the adjusting body 82 and can be screwed with a female screw 18 </ b> A formed in the main body casing 18. A groove 82A into which a driver or the like (not shown) can be inserted is formed at the end of the adjustment body 82, and the screwing depth of the adjustment body 82 into the main body casing 18 is changed by the rotation of the adjustment body 82 by the driver. Thus, the overall length of the spring 81 changes, and the urging force of the spring 81 against the ball 80 is adjusted.
[0040]
In the embodiment, the difference between the static friction and the dynamic friction, or the difference between the starting efficiency and the operating efficiency is more actively utilized in the configuration. That is, in the present embodiment, as the speed reduction mechanism of the speed reducer (power transmission device) 14 that is intended to have the reverse rotation prevention function, basically, the swing speed reduction portion G2 having an activation efficiency of about 70% is employed. Here, the starting efficiency means that when a predetermined rotational torque is applied to the input shaft while the output shaft is stopped, a value (100%) obtained by multiplying the rotational torque by a reduction ratio is generated on the output shaft. This is equivalent to η when only η% can be taken out. In the same power transmission device, the value is reproducible.
[0041]
An activation efficiency of about 70% means that the operation efficiency is higher. The operating efficiency changes depending on the magnitude of the load at that time, the rotational speed, or the like, but does not become lower than the starting efficiency. That is, the operating efficiency of the rocking speed reduction part G2 according to the present invention is at least 70% or more. In this embodiment, since the two-stage parallel shaft gear reduction part G1 is provided upstream of the swing reduction part G2, the starting efficiency of the reduction mechanism as a whole is 80% (the pinion 30 and the first gear 32). ) × 80% (second pinion 33 and second gear 34) × 70% (swinging reduction part G2) = 44.8%, and the starting efficiency is 40% or more.
[0042]
Next, the operation of the speed reducer 14 according to the first embodiment will be described.
[0043]
When the motor shaft 13 of the motor 12 rotates, the pinion 30 formed at the tip of the motor shaft 13 rotates. This rotation is transmitted in the order of the first gear 32 meshed with the pinion 30, the intermediate shaft 31, and the second pinion 33, and the second gear 34 (on the eccentric body 42) rotates. When the second gear 34 rotates, the eccentric body 42 integral with the second gear 34 rotates around the support shaft 38 while being supported by the roller bearing 40.
[0044]
When the eccentric body 42 rotates, the external gear 46 tries to oscillate and rotate around the eccentric body 42, but its rotation is suppressed by the internal gear 48 integrated with the main body casing 18. The tooth gear 46 only swings while being inscribed in the internal gear 48. However, since the number of teeth “43” of the external gear 46 is one less than the number of teeth “44” of the internal gear 48, the external gear 46 rotates with respect to the internal gear 48 every rotation of the eccentric body 42. The tooth number difference “1” is shifted (rotates). This means that one rotation of the eccentric body 42 is decelerated to rotation of the external gear 46 by −1 / 43 = −1 / 43. The minus sign indicates that the rotation direction of the external gear 46 is opposite to the rotation direction of the eccentric body 42.
[0045]
The swinging rotation of the external gear 46 is absorbed by the clearance between the through hole 47 and the inner roller 70, and only the rotation component is transmitted to the output shaft 56 via the inner pin 72.
[0046]
Here, in this embodiment, the operating efficiency of the speed reducer 14 is at least higher than that due to the characteristic that the starting efficiency is about 40%, while the starting efficiency is lowered by the frictional force applying mechanism F1. . Since the frictional force applied to the sliding portion 78S by the frictional force applying mechanism F1 is drastically reduced when the speed reduction mechanism starts to rotate, the speed reducer 14 can be operated taking advantage of its original high efficiency.
[0047]
That is, when the drive target device (not shown) is stopped, that is, when the operation is to be resumed from when the speed reducer 14 is stopped, the maximum static friction inherent in the speed reduction mechanism is reduced. Unless the reverse torque greater than the value obtained by adding the maximum static friction applied by the frictional force applying mechanism F1 is applied from the load side, the speed reducer 14 maintains the stopped state (self-locking function).
[0048]
On the other hand, once the speed reducer 14 starts rotating, not only the rotational efficiency is increased by the difference between the dynamic friction force inherent in the speed reduction mechanism and the static friction force so far, but also the friction force applying mechanism. The rotational efficiency is increased by the difference between the dynamic friction force in F1 and the static friction force until then, and the speed reducer 14 is operated in a state where the original high rotational efficiency is utilized.
[0049]
Since the friction application by the frictional force application mechanism F1 is always performed, the self-lock function is automatically exhibited not only when the normal operation is stopped, but also when the device is stopped due to an unexpected accident such as a power failure. .
[0050]
In the first embodiment, the frictional force imparting mechanism F1 is disposed with respect to the first gear 32, which is a rotating member located on the upstream side of the swing reduction part G2 on the power transmission path. Since the rotation of the output shaft 56 can be prevented by force, the configuration of the frictional force applying mechanism F1 can be reduced in size and cost, and the efficiency reduction during operation can be reduced.
[0051]
Further, the frictional force applying mechanism F1 can adjust and change the sliding resistance between the bush 78 and the second intermediate shaft 76, that is, the magnitude of the frictional resistance applied to the first gear 32. Depending on the specific application, it is possible to make fine adjustments in the field in consideration of the balance between required self-locking property and rotational smoothness.
[0052]
In the first embodiment, a support shaft 38 that simply supports the eccentric body 42 is disposed at the center of the swing reduction part G2. The support shaft 38 does not have a function as an input shaft as in the prior art, but instead is integrated coaxially with the output shaft 56 and has a function as an extension of the output shaft 56. Therefore, by supporting the support shaft 38 together with the output shaft 56 with bearings 50 and 55, it is possible to secure the support rigidity of the support shaft 38 that is the rotation base of the eccentric body 42 and to secure the support rigidity of the output shaft 56. It can be realized at the same time. As a result, it is possible to obtain the swing reduction portion G2 of the intermeshing planetary gear structure having a simple structure, a small number of parts, and high support rigidity.
[0053]
Next, the geared motor 100 to which the power transmission device according to the example of the second embodiment of the present invention is applied will be described in detail with reference to FIGS. 5 and 6 are cross-sectional views corresponding to FIGS. 1 and 2 and a plan view thereof, and FIG. 7 is an enlarged view of the cross section in the vicinity of the manual operation shaft 102.
[0054]
The geared motor 100 includes a manual operation shaft 102 that can manually rotate the output shaft 56 and replaces the frictional force applying mechanism F1 of the geared motor 10 described above with respect to the manual operating shaft 102. Is arranged. In addition, about the part similar to the said geared motor 10, while attaching | subjecting the same code | symbol in a figure, the description is abbreviate | omitted.
[0055]
As shown in FIG. 7, the manual operation shaft 102 is rotatably supported by the end cover 20 and the main body casing 18 via a pair of bearings 104 and 106 having an L-shaped cross section. Further, a fourth pinion 102A that meshes with the second gear 34 of the parallel shaft gear reduction portion G1 is integrally formed between the bearings 104 and 106 of the manual operation shaft 102. Further, a hexagon bolt shaft 102B is integrally formed at the tip of the manual operation shaft 102 on the upper side in the drawing, and the fourth pinion is obtained by rotating the hexagon bolt shaft 102B with a tool such as a hexagon wrench. The output shaft 56 can be manually rotated via the 102A, the second gear 34, and the swing reduction part G2.
[0056]
The frictional force applying mechanism F2 disposed on the manual operation shaft 102 includes a brake case 108 fixed to the end cover 20, and a pair of first and second fixing plates 110 are provided in an inner space of the brake case 108. 112, a rotating plate 114 disposed between the pair of first and second fixed plates 110, 112, and a spring contracted between the first fixed plate 110 and the inner peripheral surface of the brake case 108. 116 is accommodated.
[0057]
The pair of first and second fixing plates 110 and 112 are each made of a substantially disk-shaped member that is coaxially disposed on the outer periphery in the radial direction of the manual operation shaft 102. Spline grooves 110A and 112A are formed on the outer peripheral portions of the first and second fixing plates 110 and 112, respectively. The spline grooves 110A and 112A are fitted into the spline 108A integrally formed on the inner peripheral portion of the brake case 108. The first and second fixing plates 110 and 112 can move in the axial direction (vertical direction in the drawing) and cannot rotate relative to the manual operation shaft 102.
[0058]
On the other hand, the rotating plate 114 disposed between the first and second fixed plates 110 and 112 is a substantially disk-shaped member having an outer diameter smaller than the inner diameter of the spline 108A of the brake case 108. A spline groove 114A that fits with a spline 102C formed on the outer peripheral portion of the manual operation shaft 102 is formed on the inner peripheral portion of the rotary plate 114, and the rotary plate 114 is movable in the axial direction. The structure is rotatable with the manual operation shaft 102.
[0059]
The rotating body 114 is sandwiched between a first fixing plate 110 urged toward the rotating body 114 by a spring 116 and a second fixing plate 112 that is in contact with a spacer 118 provided in the brake case 108. In this state, friction is slid along with the rotation of the manual operation shaft 102. Further, the biasing force of the spring 116 can be adjusted by changing the thickness of the spacer 118, thereby adjusting the sliding resistance (frictional force) between the rotating body 114 and the first and second fixing plates 110, 112. It can be changed. Therefore, if several types of spacers 118 having various thicknesses are prepared, it is possible to make fine adjustments in the field in consideration of the balance between required self-locking property and rotational smoothness according to specific applications. Become.
[0060]
According to the geared motor 100 to which the power transmission device according to the second embodiment of the present invention is applied, the same effect as the geared motor 10 can be obtained by slightly improving the existing power transmission device.
[0061]
8 to 10 are views showing a solar power generation apparatus to which the geared motor 100 is applied, FIG. 8 is an overall view of the solar power generation apparatus, and FIGS. 9 and 10 are enlarged views of the geared motor in FIG.
[0062]
This solar power generation device 120 includes a horizontally long rectangular solar cell panel 122, a first geared motor 100A that rotationally drives the solar cell panel 122 via a pipe-shaped horizontal shaft 124, the solar cell panel 122, the geared motor 100A, and the like. And a second geared motor 100 </ b> B that rotationally drives the horizontal support 126 via a column member 127.
[0063]
As shown in FIG. 9, the first geared motor 100A can drive the pipe-shaped horizontal shaft 124 in the direction R1 in the drawing. Accordingly, the solar cell panel 122 is driven to rotate in both forward and reverse directions via the pipe-shaped horizontal shaft 124, and its reverse rotation is prevented by the self-locking function of the first geared motor 100A, so that an unexpected accident such as a power failure is caused. Even when the solar power generation device 120 is stopped by the above or the like, the stopped state of the solar cell panel 122 is maintained.
[0064]
Further, as shown in FIG. 10, the second geared motor 100B can drive the pinion shaft 128 connected to the output shaft 56 in the direction R2 in the drawing. Accordingly, the horizontal support 126 is driven to rotate in both forward and reverse directions via the pinion shaft 128 and the support member 127, and its reverse rotation is prevented by the self-locking function of the second geared motor 100B. Even when the photovoltaic power generation device 120 is stopped due to an accident or the like, the stopped state of the horizontal support 126 is maintained.
[0065]
In the examples of the first and second embodiments, the speed reduction mechanism has the characteristics that the efficiency during operation is relatively high and the startup efficiency is relatively low (still about 70%). Although the swing reduction part G2 of the meshing planetary gear structure is applied, the present invention is not limited to this. In short, as long as the overall startup efficiency is 40% or more, other reduction mechanisms can be applied. Good.
[0066]
Further, the frictional force applying means according to the present invention is not limited to the structure and arrangement of the frictional force applying mechanisms F1 and F2 in the examples of the first and second embodiments, but the power transmission path of the speed reducing mechanism. Any frictional force applying means that can always apply a frictional resistance to any rotating member on the power transmission path during operation is disposed at any of the above positions.
[0067]
【The invention's effect】
ADVANTAGE OF THE INVENTION According to this invention, while having a high self-locking function, the power transmission device which can improve the rotation efficiency of the whole apparatus simultaneously can be provided.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a geared motor to which a power transmission device according to a first embodiment of the present invention is applied.
FIG. 2 is a diagram showing a plan view of the geared motor in FIG.
FIG. 3 is a diagram showing a cross section of a rocking speed reducing portion in FIG.
4 is a cross-sectional view taken along line IV-IV in FIG.
FIG. 5 is a cross-sectional view of a geared motor to which a power transmission device according to a second embodiment of the present invention is applied.
6 is a plan view of the geared motor in FIG. 5;
7 is an enlarged view showing a cross section near the manual operation shaft in FIG.
FIG. 8 is a diagram showing an entire photovoltaic power generation apparatus to which a geared motor according to a second embodiment of the present invention is applied.
9 is an enlarged view of the first geared motor in FIG.
10 is an enlarged view of the second geared motor in FIG.
FIG. 11 is a diagram showing an entire conventionally known photovoltaic power generation apparatus.
[Explanation of symbols]
G1 ... Parallel shaft gear reduction part
G2: Oscillating speed reducer
WG1, WG2 ... Worm gear set
F1, F2 ... Friction force applying mechanism
1, 120 ... Solar power generation device
2, 122 ... solar cell panel
3, 124 ... Pipe-shaped horizontal axis
4, 8 ... drive motor, second drive motor
6, 126 ... Horizontal support stand
7, 127 ... support members
5, 9 ... reduction gear group, second reduction gear group
10, 100, 100A, 100B ... Geared motor
12 ... Motor
13 ... Motor shaft
14 ... Reducer
16, 29 ... casing
18 ... Body casing
20 ... end cover
24 ... Bolt
30 ... Pinion
31 ... Intermediate shaft
32 ... 1st gear
33 ... Second pinion
34 ... Second gear
38 ... Support shaft
40, 44 ... Roller bearing
42. Eccentric body
46 ... External gear
47 ... Inner pin hole
48 ... Internal gear
49 ... pin
50, 55, 83, 84, 104, 106 ... bearings
56 ... Output shaft
58 ... Flange body
70 ... Inner roller
72 ... Inner pin
76 ... Second intermediate shaft
77 ... The third pinion
78 ... Bush
80 ... Ball
81, 116 ... spring
82 ... Regulator
85 ... Male thread
102 ... Manual operation axis
102A ... 4th pinion
108 ... Brake case
110, 112 ... first and second fixing plates
114 ... Rotating plate
120 ... Solar power generation device
128 ... pinion shaft

Claims (5)

A power transmission having a reverse rotation prevention function including a speed reduction mechanism including an input shaft and an output shaft, and having a function of preventing the output shaft from reversing when a torque for reversing the output shaft is applied from the load side. In the device
As the speed reduction mechanism, a start-up efficiency is 40% or more , and the speed reduction mechanism alone does not exhibit the reverse rotation prevention function .
At any position on the power transmission path of the speed reduction mechanism, a frictional force applying means capable of always applying resistance due to friction to any rotating member on the power transmission path during operation is disposed,
The power transmission device having an anti-reverse function, wherein the anti-reverse function is exhibited only when a frictional force is always applied to the rotating member by the frictional force applying means in a stopped state. In claim 1,
The speed reduction mechanism includes at least a speed reducing portion of a swinging intermeshing planetary gear structure including an external gear and an internal gear having a slight difference in the number of teeth.
A power transmission device having a reverse rotation preventing function. In claim 2,
The power transmission device having an anti-reverse function, wherein the frictional force applying means is disposed on the rotating member located on the upstream side of the speed reducing portion of the planetary gear structure. In any one of Claims 1-3, Furthermore,
The power transmission device includes a manual operation shaft capable of manually rotating the output shaft,
A power transmission device having an anti-reverse function, wherein the frictional force applying means is disposed with respect to the manual operation shaft. In any one of Claims 1-4,
A power transmission device having a reverse rotation prevention function, wherein a magnitude of a frictional resistance applied to the rotating member by the frictional force applying means can be adjusted and changed.

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