JP5701351B2 - Orthogonal gear motor - Google Patents

Description

  The present invention relates to a gear motor composed of a motor and a speed reducer, and in particular, an orthogonal gear motor (hereinafter simply referred to as “gear motor”) in which the axial direction of the input shaft of the motor and the axial direction of the output shaft of the speed reducer are orthogonal. )

  In the gear motor, torque from the input shaft of the motor is transmitted through a gear mechanism (hereinafter referred to as “orthogonal shaft gear mechanism”) in which gears such as a worm gear, bevel gear, hypoid gear, and face gear are orthogonal to each other in the axial direction. There is an orthogonal gear motor configured such that the axial direction of the final output shaft is orthogonal to the axial direction of the input shaft of the motor. Examples of such orthogonal gear motors include those shown in Patent Documents 1 and 2.

JP 2012-80771 A JP 2003-278846 A

  The gear motor of Patent Document 1 has a pinion gear formed on the input shaft of the motor, and a face gear composed of a gear whose axial direction is orthogonal to the pinion gear, and a hollow output shaft (through a parallel shaft gear mechanism through a plurality of stages. Torque is transmitted to the final output shaft. The width of the gear motor housing (dimension in the axial direction of the final output shaft) is approximately the same width as the outer diameter of the gear case, as with a general orthogonal gear motor, so the driven shaft is inserted into the hollow output shaft. In this case, a space for attaching the end plate to the side opposite to the insertion direction of the driven shaft is required. Therefore, a space larger than the width of the motor and the gear case is required at the installation location of the gear motor.

  The gear motor of Patent Document 2 has a first input gear formed on the input shaft of the motor, a first output gear whose axial direction is orthogonal to the first input gear, and is provided on the gear shaft of the first output gear. The torque is transmitted from the second input gear to the final output shaft through the parallel gear. In the case of this gear motor, since the housing is formed in an L shape, the housing can be made compact in the axial direction of the final output shaft, and a space can be secured accordingly.

In recent years, gear motors are required to be compact enough to be installed in a small space, and in order to meet this demand, it is necessary to make the speed reducer compact.
In the case of the gear motor of Patent Document 1, as described above, the width of the housing is almost the same as the width of the motor case, and the compactness is lacking.
In the case of the gear motor of Patent Document 2, the housing is formed in an L shape to achieve compactness. However, the gear shaft of the first output gear is the first output gear and the second input as viewed from the input shaft. Since it is a structure that is supported in a cantilever state only by a bearing provided at the tip of the gear, that is, only a bearing located on one side in the axial direction when viewed from the first output gear, Still, the width of the housing tends to increase outward in the radial direction of the motor when viewed from the input shaft of the motor.
In addition, the gear motor preferably includes an overload protection device for interrupting torque transmission and preventing damage to the device when an overload due to the driven device, for example, a conveyed product is jammed in the conveyor, When this overload protection device is provided, it is difficult to achieve compatibility with the compactness of the gear motor.

  In view of the above-described problems of the prior art, it is an object of the present invention to provide a more compact gear motor and to maintain compactness even when an overload protection function is provided. It is a further object to provide a gear motor that can be used.

The present invention includes a motor having a motor case;
A housing in which the motor is mounted, and is housed in the housing;
A first input gear provided on an input shaft from the motor;
Meshed with the first input gear, a first output gear orthogonal to the first input gear in the axial direction;
A first bearing and a second bearing which are arranged in front and rear in the axial direction of the first output gear, and which support the gear shaft of the first output gear;
A second input gear provided on the first bearing side on the gear shaft of the first output gear;
In a gear motor having a hollow final output shaft to which torque from the second input gear is transmitted,
The first input gear is a worm gear, and the first output gear is a worm wheel;
The housing includes a torque arm for fixing the gear motor to an installation location;
The second bearing, in the axial direction of the final output shaft, located in the range of up to an outer diameter of the shaft center the motor case of said input shaft,
The final output shaft in the axial direction passes through the axial center of the input shaft and the axial center of the first output gear , and is on the second input gear side from a plane orthogonal to the axial direction of the final output shaft. The problem is solved by an orthogonal gear motor, characterized in that the end face of the final output shaft does not protrude from the face .

According to the present invention, a compact gear motor can be obtained. That is, the gear motor of the present invention meshes so that the first input gear provided on the input shaft from the motor (including the case of being connected) and the first output gear are orthogonal to their axial directions. In other words, the first-stage gear mechanism as viewed from the motor has an orthogonal shaft gear mechanism. The first bearing and the second bearing are arranged in front and rear in the axial direction of the first output gear, and the second bearing extends from the axis of the input shaft to the outer diameter of the motor case in the axial direction of the final output shaft . since a structure that is located in range, (the axial dimension of the final output shaft) width of the housing in the first stage gear unit as viewed from the motor can be made compact. In addition, since the housing includes a torque arm for fixing the gear motor to the installation location, it is possible to reduce a radial load caused by the driven device connected to the driven shaft, which is applied to the output shaft and the output shaft bearing. Therefore, the distance between the pair of output shaft bearings can be reduced. Then, the final output shaft in its axial direction through the axial center of the axis and the first output gear of the input shaft, is disposed on the second input gear side than the axial direction perpendicular to the plane of the gear shaft, final Since the end surface of the output shaft does not protrude from the surface , the housing can be formed in an L shape, so that the housing of the final output shaft portion can be made compact in the axial direction, and a space can be secured accordingly.

  In addition, an overload protection device is provided in the gap between the first output gear and the second bearing, and the housing of the portion that houses the overload protection device has an outer diameter of the motor case in the axial direction of the final output shaft. If the configuration falls within this range, the gear motor having an overload protection function can be obtained while maintaining the compactness of the housing.

  Furthermore, if the sensor mechanism for detecting the operation of the overload protection device is provided outside the housing ahead of the second bearing as viewed from the overload protection device, the torque transmission can be cut off only when an overload occurs. In addition, an alarm signal for transmitting the occurrence of overload can be transmitted, or the motor can be stopped.

  Further, if the sensor detection part of the sensor mechanism is configured to be within the range of the outer diameter of the motor case in the axial direction of the final output shaft, the structure with the sensor mechanism is maintained and the compactness of the housing is maintained. be able to.

  In addition, if it is configured to have a space portion in the range up to the outer diameter of the motor case on the opposite side of the final output shaft with respect to a surface that passes through the input shaft axis and is orthogonal to the gear shaft axis center, It is possible to secure a work space such as attaching to the final output shaft.

  Further, if the input shaft and the final output shaft are arranged on the same plane, the gear motor has a height dimension (the radial dimension of the motor perpendicular to the axial direction of the final output shaft). In addition, the housing that houses from the first input gear to the final output shaft has four surfaces, one on the input shaft side in the radial direction of the final output shaft, other than the surface on the input shaft side. If the distance between the surface and the axis of the final output shaft is the same, the size of the housing can be minimized with respect to the radial direction of the final output shaft.

  In addition, if the housing in which the final output shaft is accommodated is within the range of the fan cover of the motor in the radial direction of the motor perpendicular to the axial direction of the final output shaft, Can also be made compact.

  Further, in the housing in which the first input gear to the final output shaft are accommodated, the compartment in which the first input gear is accommodated communicates with the compartment in which the second input gear and the gear meshing therewith are accommodated. If it is set as a structure, since lubricating oil circulates and lubrication of each gear can be performed efficiently, it is suitable.

  If the second input gear is positioned between the first bearing and the second bearing, the stability of the gear shaft of the first stage gear mechanism can be improved, while the second input gear If the configuration is located at the tip of the first bearing as viewed from the first output gear, the width of the housing in the first gear portion can be made more compact.

The top view (a) of 1st embodiment of this invention, and a front view (b). The perspective front view of the principal part of 1st embodiment of this invention. The cross-sectional view of the principal part of 1st embodiment of this invention. (A) is the sectional view on the 4a-4a line of FIG. 2, (b) is the sectional view on the 4b-4b line. The cross-sectional view of the principal part of 2nd embodiment of this invention. The top view (a) of 3rd embodiment of this invention, and a front view (b). The cross-sectional view of the principal part of 3rd embodiment of this invention. The cross-sectional view of the main part of the fourth embodiment of the present invention.

  An embodiment of the present invention will be described with reference to FIGS. However, the present invention is not limited to this embodiment.

  As shown in FIG. 1, the gear motor 10 includes a motor M and a speed reducer G, and a bolt V is inserted into a torque arm fixing hole 18 a of a torque arm 18 attached to the housing 15 to be fixed at an installation location. The As described above, if the torque arm 18 is attached to the housing 15 and the gear motor 10 is fixed to the installation place by using the torque arm 18, the output shaft 34 and the output shaft bearing 38 (see FIG. 3) are applied. Since the radial load caused by the driven device (not shown) connected to the driven shaft 14 can be reduced, it is preferable because the distance between the pair of output shaft bearings 38 can be reduced. As a method for attaching the torque arm 18 to the housing 15, if the bolts are provided at equal intervals in the circumferential direction in each of the housing 15 and the torque arm 18 and are attached with fixing bolts, the torque arm for the housing 15 is provided. Since the mounting angle of 18 can be changed, the position of the torque arm fixing hole 18a can be changed afterwards. The torque arm 18 may be formed integrally with the housing 15, and the positions of the torque arm 18 and the torque arm fixing hole 18a can be changed as appropriate in addition to the illustrated positions.

  The motor M includes a terminal box 12 and a motor case 13 that are attached as necessary, and the speed reducer G includes a first-stage gear unit 20. The shape of the housing 15 including the first gear portion 20 of the speed reducer G is L-shaped in a plan view as shown in FIG. As shown in FIG. 1B, the final output shaft 34 located at the long side portion is arranged so that the oil seal 36 does not overlap the first gear portion 20. Of course, the present invention can be applied to a solid final output shaft.

  As shown in FIG. 2, the speed reducer G is provided on the input shaft 11 from the motor (including a case where it is connected), a worm gear (first input gear) 22, and a worm wheel that meshes with the worm gear 22. (First output gear) 24, a helical pinion gear (second input gear) 26 provided on the gear shaft 21 on which the worm wheel 24 is provided, a final output gear 32 meshing with the helical pinion gear 26, and a hollow final An output shaft 34 is provided, and these are accommodated in the housing 15. As is apparent from the figure, if the input shaft 11 and the final output shaft 34 are arranged on the same plane, the height of the gear motor 10 (the direction perpendicular to the axial direction of the final output shaft 34) is assumed. The dimension of the motor M in the radial direction can be minimized. Further, the housing 15 has four surfaces 15a to 15d, one side of which is the input shaft 11 side, in the radial direction of the final output shaft 34, and the surfaces 15b to 15d other than the surface 15a on the input shaft 11 side and the final output. If the distance between the shaft 34 and the shaft center is equal, the size of the housing 15 can be minimized with respect to the radial direction of the final output shaft 34. Note that the first stage gear mechanism starting from the input shaft 11 may be a bevel gear, a hypoid gear, a face gear, or the like in addition to the worm gear mechanism as long as it is an orthogonal shaft gear mechanism. Further, as long as the input shaft 11 and the final output shaft 34 are orthogonal to the axial direction, a gear mechanism may be further provided between the second input gear and the final output gear.

FIG. 3 is a cross-sectional view of a main part of the gear motor 10. Lubricating oil is enclosed in the speed reducer G, and the airtightness of the speed reducer G is maintained by an oil seal 36 or the like provided in the final output shaft 34 portion. In the case of FIG. 3, the motor case 15 and the torque arm 18 are integrated. As shown in FIG. 3, a first bearing 23 and a second bearing 25 are provided in the axial direction of the worm wheel 24 that meshes with the worm gear 22, and the second bearing is in the axial direction of the final output shaft 34. Since the shaft center X of the input shaft 11 (that is, the shaft center of the worm gear 22) to the outer diameter X2 of the motor case 13 is positioned on the input shaft 11 side from the middle X3, the first gear portion 20 The width of the housing 15 (the dimension in the axial direction of the final output shaft 34) can be reduced. Further, since the helical pinion gear 26 as the second input gear is provided on the gear shaft 21 of the worm wheel 24 at the tip of the first bearing 23 when viewed from the worm wheel 24, the width of the housing in the first stage gear portion. In particular, it can be made more compact with respect to the helical pinion gear 26 side as viewed from the input shaft 11.

As shown in FIGS. 2 and 3, the final output shaft 34 passes through the axial center X of the input shaft 11 and the axial center of the first output gear 24 in the axial direction, and the shaft of the final output shaft 34. Since the end face of the final output shaft 34 is not projected from the surface disposed on the helical pinion gear 26 side from the surface orthogonal to the direction , the housing 15 of the final output shaft 34 portion can be made compact in the axial direction. Thus, the space S can be secured correspondingly, and the end plate 16 (see FIG. 1) can be easily attached and detached.

  Further, since the gear shaft 21 is stably supported by providing the gap T between the worm wheel 24 and the second bearing 25, the vibration of the helical pinion gear 26 can be suppressed, and the helical pinion gear can be suppressed. It is possible to improve the contact stability with respect to the 26 final output gears 32. Similarly, a gap T can be provided between the worm wheel 24 and the first bearing 23, but the helical pinion gear 26 and the final output gear 32 are provided from the input shaft 11 (see FIG. 2) by the amount of the gap. Since the housing 15 protrudes beyond the motor case 13 (see FIG. 1) of the motor M in some cases, the gap T is formed between the worm wheel 24 and the second bearing 25. Between the two.

  4A and 4B, the housing 15 includes a section 19 in which the worm gear 22 is stored, and a section 19a in which the helical pinion gear 26 and the final output gear 32 that meshes with the section 19a are stored. A lubricating oil recirculation hole 17 that communicates is provided. In this way, if the section in which the first input gear is housed and the section in which the second and subsequent gears are housed are communicated with each other, as shown in FIG. Since the lubricating oil circulates between the gears, each gear can be lubricated efficiently.

  FIG. 5 is a cross-sectional view of the main part when the overload protection device 40 is provided in the first-stage gear mechanism according to the second embodiment of the present invention. Since the basic configuration is the same as that of the first embodiment, the description of the same parts is omitted. As shown in FIG. 5, the overload protection device 40 is provided with a driven flange 42 on the gear shaft 21 of the worm wheel 24, and the ball 44 is formed on the side surface of the worm wheel 24 and on the side surface of the driven flange 42. It is configured by holding the driven flange 42 in the direction of the worm wheel 24 with an elastic member (coil spring) 46 while being held between the formed recesses. When the above-described bevel gear or the like is used as the first-stage gear mechanism, a recess for fitting the ball 44 may be formed on the back surface (the surface where no gear is formed) of the first output gear. Thus, if the gap T is provided between the worm wheel 24 and the second bearing 25 and the overload protection device 40 is provided in the gap T, the stability of the gear shaft 21 and the helical pinion gear 26 is improved. The overload protection device 40 can be maintained, and the portion of the housing 15 that accommodates the overload protection device 40 is within the outer diameter of the motor case 13 in the axial direction of the final output shaft 34. A compact gear motor having a protective function can be obtained. Although it is assumed that an overload protection device is attached to the final output gear 32, since the final output gear 32 has a relatively large diameter, a large overload protection device corresponding to a large torque must be used. Of course, the manufacturing cost will increase accordingly. Even if the overload protection device is provided on the torque arm 18 side or the opposite side of the final output gear 32, the axial dimension of the final output shaft 34 is increased. As a result, the length of the final output shaft 34 itself is increased. Since it will also be long, it will lack compactness. The operation of the overload protection device 40 is not described because it is different from the gist of the present invention, but as the overload protection device 40, in addition to the illustrated ball type, depending on the case, a friction type, A roller type or a cam type can be applied.

  FIG. 6 is a diagram showing a third embodiment of the present invention. Since the basic configuration is the same as that of the first and second embodiments, the description of the same parts is omitted. Since the basic configuration is the same, the housing 15 can be shared between the first to third embodiments. As shown in FIG. 6, the gear motor 10 a includes an overload protection device 40, and further, viewed from the overload protection device 40, the housing is in the axial direction and ahead of the second bearing 25 (see FIG. 4). 15 is provided with a sensor mechanism 50 that detects the operation of the overload protection device 40. The gear motor 10a is suitable because it can transmit a signal for issuing an alarm when the overload protection device 40 is activated, or can automatically stop the operation of the motor M.

  In addition, a driven device (not shown) such as a conveyor is connected to the driven shaft 14 connected to the final output shaft 34. In such a case, the height dimension of the gear motor 10a is compact. As shown in FIG. 6B, the dimension D in the height direction of the housing 15 is within the range of the dimension E in the same direction of the fan cover 13a of the fan (not shown) provided in the motor M. If it is set as the structure which fits in, the compactness along the said request | requirement is realizable. In addition, as shown in FIG. 6, the cover C for preventing entanglement in the drive unit such as the connecting portion of the final output shaft and the conveyor can be accommodated in the height direction dimension of the motor case 13. Even when the cover C is attached, the compactness can be maintained. If the terminal box 12 is provided in the same direction as the axial direction of the gear shaft 21 (see FIG. 6) of the first output gear 24, the height of the gear motor 10a can be minimized. The same applies to the first and second embodiments.

  In addition, the sensor mechanism 50 is provided so as to be axially viewed from the worm wheel 24, ahead of the overload protection device 40, and so as not to cover the oil seal 36 of the final output shaft 34. The maintenance work of the sensor mechanism 50, the overload protection device 40, the first gear portion 20, and the final output shaft 34 can be approached from the same direction.

  As shown in FIGS. 6 and 7, the sensor mechanism 50 is provided outside the housing 15. Thereby, the sensor mechanism 50 is isolated from the storage part of each gear, and can prevent contamination by the lubricating oil that lubricates each gear. Further, as shown in the drawing, the entire sensor mechanism 50 is preferably covered with a sensor case 55 to protect it from external dust and the like. In the case of the figure, the sensor case 55 includes a sensor case wall portion 55a continuously extending from the housing 15 and a sensor case lid portion 55b. At this time, it is preferable to provide the sensor case 55 so as not to cover the oil seal 36 of the final output shaft 34 from the viewpoint of improving maintenance.

  The sensor mechanism 50 includes a limit switch 52, a limit switch lever 51, and a limit switch shaft 56. The limit switch shaft 56 communicates with the inside of the first-stage gear mechanism 20, and its end is located at a small distance from the side surface of the driven flange 42 on the elastic member 46 side. When the overload protection device 40 is activated, the ball 44 rides on the worm wheel 24 and the driven flange 42, so that the driven flange 42 moves in a direction to urge the elastic member 46 and pushes the limit switch shaft 56. The limit switch shaft 56 is provided with a washer 58. When the washer 58 hits the limit switch lever 51, the limit switch 52 is operated. Thus, the signal from the limit switch 52 is emitted to the outside through the lead wire 54. When the operating state of the overload protection device 40 is released, the washer 58 is pushed back by the return spring 53 provided on the limit switch shaft 56 and automatically returns to the normal state. Needless to say, another sensor mechanism such as a proximity switch can be used instead of the limit switch. Here, as shown in the figure, the sensor detection unit of the sensor mechanism 50 may be configured to be within the range of the outer diameter of the motor case 13 in the axial direction of the final output shaft 34. The sensor detection unit refers to a limit switch lever 51 in the case of a limit switch and a detection surface in the case of a proximity switch.

  FIG. 8 is a cross-sectional view showing the main part of the fourth embodiment of the present invention. As shown in FIG. 8, the helical pinion gear 26 may be positioned between the first bearing 23 and the second bearing 25. By doing so, it is possible to improve the stability of the gear shaft on which the helical pinion gear 26 is provided. This configuration can be applied to any of the embodiments described above.

  As described above, according to the present invention, the size of the housing in the axial direction of the final output shaft can be reduced, and the operation of the overload protection device and the overload protection device can be performed while maintaining compactness. It can be set as the gear motor which provides the sensor mechanism to detect.

10, 10a Orthogonal gear motor 11 Input shaft 12 Terminal box 13 Motor case 13a Fan cover 15 Housing 19, 19a Partition 21 Gear shaft 22 First input gear (worm gear)
23 First bearing 24 First output gear (worm wheel)
25 Second bearing 26 Second input gear 34 Final output shaft 40 Overload protection device 50 Sensor mechanism 51 Sensor detector (limit switch lever)
X Input shaft axis X2 Motor case outer diameter X3 Between X and X2

Claims (10)

A motor having a motor case;
A housing in which the motor is mounted, and is housed in the housing;
A first input gear provided on an input shaft from the motor;
Meshed with the first input gear, a first output gear orthogonal to the first input gear in the axial direction;
A first bearing and a second bearing which are arranged in front and rear in the axial direction of the first output gear, and which support the gear shaft of the first output gear;
A second input gear provided on the first bearing side on the gear shaft of the first output gear;
In a gear motor having a hollow final output shaft to which torque from the second input gear is transmitted,
The first input gear is a worm gear, and the first output gear is a worm wheel;
The housing includes a torque arm for fixing the gear motor to an installation location;
The second bearing, in the axial direction of the final output shaft, located in the range of up to an outer diameter of the shaft center the motor case of said input shaft,
The final output shaft in the axial direction passes through the axial center of the input shaft and the axial center of the first output gear , and is on the second input gear side from a plane orthogonal to the axial direction of the final output shaft. And the end face of the final output shaft does not protrude from the face ,
Orthogonal gear motor. Comprising an overload protection device between the first output gear and the second bearing;
2. The orthogonal gear motor according to claim 1, wherein a housing of a portion housing the overload protection device is within a range of an outer diameter of the motor case in an axial direction of the final output shaft.   The orthogonal gear motor according to claim 2, wherein a sensor mechanism for detecting the operation of the overload protection device is provided outside the housing ahead of the second bearing as viewed from the overload protection device.   The orthogonal gear motor according to claim 3, wherein a sensor detection unit of the sensor mechanism is within an outer diameter range of the motor case in the axial direction of the final output shaft.   From the surface which passes through the axis of the input shaft and is orthogonal to the axis of the gear shaft, on the opposite side of the final output shaft, there is a space portion in a range up to the outer diameter of the motor case. The orthogonal gear motor according to any one of 4.   The axis of the input shaft and the final output shaft are located on the same plane, and the housing has four surfaces with the input shaft side as one side in the radial direction of the final output shaft. 6. The orthogonal gear motor according to claim 1, wherein a distance between a surface other than the surface and the axis of the final output shaft is equal. The motor has a fan cover;
The orthogonal gear motor according to any one of claims 1 to 6, wherein a dimension of the housing in the radial direction of the motor perpendicular to the axial direction of the final output shaft is within the outer diameter of the fan cover.   The orthogonal gear motor according to any one of claims 1 to 7, wherein a section in which the first input gear is housed communicates with a section in which the second input gear and a gear meshing with the second input gear are housed.   The orthogonal gear motor according to any one of claims 1 to 8, wherein the second input gear is located at the tip of the first bearing as viewed from the first output gear.   9. The orthogonal gear motor according to claim 1, wherein the second input gear is located between the first bearing and the second bearing.

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