WO2015129455A1

WO2015129455A1 - Motor unit

Info

Publication number: WO2015129455A1
Application number: PCT/JP2015/053695
Authority: WO
Inventors: 酒井　大輔
Original assignee: 日本電産サンキョー株式会社
Priority date: 2014-02-28
Filing date: 2015-02-10
Publication date: 2015-09-03
Also published as: CN104879447A; KR101673074B1; JP2015163012A; KR20150102702A; CN204921856U

Abstract

Provided is a motor unit (1) capable of preventing breakage/deformation of a worm, even when a load application means (50) being a worm gear mechanism that applies a load to gear train rotation is attached to a case (82) manually. Specifically, a load when a worker grasps the load application means (50) using their fingers is supported by an upper frame (551) and worm breakage/deformation is prevented, as a result coupling a first bearing (53) and a second bearing (54) at a position above the support position for the worm (51), by using the upper frame (551) being the upper end section of a frame (55), in the load application means (50) which has the worm (51), the first bearing (53) and the second bearing (54) that rotatably support the worm (51), the frame (55) that couples the first bearing (53) and the second bearing (54), and a brake (52) that applies resistance to the rotation of the worm (51).

Description

Motor unit

The present invention relates to a motor unit, and more particularly, to a motor unit provided with clutch means for cutting off and connecting transmission of motor power to a driven body.

In the following Patent Document 1, a first transmission train that is a gear mechanism that transmits motor power to a driven body, and transmission of motor power by the first transmission train is in a “joint” state (the power of the motor by the transmission train). Is switched to the driven state (hereinafter the same), or “disconnected” state (the state in which the power of the motor is not transmitted to the driven body (cut off) by the transmission train; the same applies hereinafter). And a motor actuator comprising a clutch means.

The motor actuator 1 of Patent Document 1 switches the clutch means between the “disengaged” state and the “joined” state by moving the driven gear 43 in the axial direction. The second tooth portion 431 that is the helical tooth portion of the driven gear 43 meshes with the first tooth portion 422 that is the helical tooth portion of the other gear, and the third tooth portion 432 that is the worm wheel portion. Meshes with the fourth tooth portion 51 which is a worm provided with a centrifugal brake mechanism.

The driven gear 43 is always urged in a direction to bring the clutch means to the “disengaged” state, and the axial force is generated by the thrust force generated from the meshing of the helical teeth and the load applied from the fourth tooth portion 51. It moves to the other side and puts the clutch means in the “joining” state.

JP 2012-80757 A

FIG. 9 is FIG. 11 of Patent Document 1, and is a perspective view of the load applying means 50 ′ included in the motor actuator of Patent Document 1. The code | symbol shown by FIG. 9 is also attached | subjected in FIG.

The fourth tooth 51, which is a worm provided with a centrifugal brake mechanism, constitutes a part of the load applying means 50 '. Both ends in the axial direction of the fourth tooth portion 51 are supported by bearings, and these bearings are connected via a frame portion. A load portion 52 is attached to one end of the fourth tooth portion 51, and a drum 83 is formed on the bearing on the load portion 52 side. A centrifugal brake mechanism is realized by the fourth tooth portion 51, the load portion 52, and the drum 83.

When such a unit composed of a worm and a worm support member is manually incorporated into a case, an operator holds the surface opposite to the worm support surface of these bearings (hereinafter also referred to as “rear surface”) with a finger, It will be press-fitted into the case. In this case, it is natural that the force for pinching the bearing by the operator varies, and it is expected that an excessive force will be applied unexpectedly. Therefore, when the rigidity of the worm support member is insufficient, if the bearing is clamped with a certain force or more, the worm supports the force, which may cause damage or deformation of the worm.

In view of the above problems, the problem to be solved by the present invention is to provide a motor unit capable of preventing the worm portion from being damaged or deformed even when the load applying means is manually attached.

In order to solve the above problems, a motor unit of the present invention includes a motor that rotates in one direction, a first transmission train that includes one or more power transmission members that transmit power of the motor to a driven body, A clutch means for switching the power transmission by the first transmission train to a "continuous" state or a "disengaged" state, and a transmission train for transmitting the power of the motor to the clutch means, wherein the first helical tooth portion A second transmission train having a first gear formed and a second gear formed with a second helical gear meshing with the first tooth; and rotation of the second gear. Load applying means for applying a load, and the second gear is supported so as to be movable in the axial direction, and is always urged in a direction that is one of the axial directions and that causes the clutch means to be in the “disengaged” state. And meshing with the first gear from the load applying means A motor unit that moves to the other side in the axial direction against the urging force by a thrust force generated when a load is applied, and puts the clutch means in a “engaged” state. The worm wheel portion is formed, and the load applying means includes a worm portion meshing with the worm wheel portion, a first bearing and a second bearing that rotatably support the worm portion, and the first bearing. And the second bearing, and a brake part that provides resistance to rotation of the worm part, with the joint surface side of the load applying means to the case half facing down, the frame part The upper frame, which is the upper end of the first, connects the first bearing and the second bearing above the support position of the worm portion.

When incorporating the load applying means into the case half, it is assumed that the upper part of the first bearing and the second bearing (hereinafter also referred to as “bearing”) is sandwiched between fingers for the convenience of work. . Therefore, by providing the upper frame, which is the upper end of the frame part, above the worm part, and connecting the first bearing and the second bearing with such an upper frame, much of the force for holding the bearing is increased. Therefore, the load on the worm portion can be reduced.

Further, it is preferable that the frame portion connects the first bearing and the second bearing by the upper frame and a lower frame which is an opposite end portion of the upper frame. In this case, the upper frame is formed to connect the first bearing and the second bearing in parallel with the worm portion at a position above the worm portion, and the lower frame is The first bearing and the second bearing can be connected in parallel with the worm portion at a position below the worm portion. Since the bearings are supported at both the upper and lower ends of the frame part, the wobble when the bearings are clamped with fingers is reduced, so that the frame part can support the bearings stably and the efficiency of the installation work Can increase the sex.

In addition, at least one of the first bearing and the second bearing is formed separately from the frame part, and the joint surface of the upper frame and the lower frame with the bearing formed separately from the frame is provided. Is formed with a convex portion projecting on the bearing formed by the separate body, and the convex portion is fitted with a concave portion formed on the bearing formed by the separate body, thereby the frame portion and the By connecting to a separately molded bearing, it is possible to easily attach the worm part to the bearing while reducing wobbling of the bearing. Specifically, the frame portion is integrally formed with the second bearing, and the first bearing is formed with a drum for storing the brake portion, and the upper frame and the lower frame are provided with the drum. Projections projecting toward the first bearing are formed on the joint surface with the first bearing, and the projections are respectively fitted into recesses formed on the first bearing. The frame portion and the first bearing can be connected to each other.

Moreover, the said frame part has a reinforcement part between the said upper frame and the said lower frame, and the rigidity of a frame part can be improved by forming a recessed part or a through-hole in this reinforcement part. In addition, the occurrence of sink marks can be prevented, and the frame portion can be formed linearly without distortion. Specifically, the reinforcing portion may be configured by providing the through hole so as to reinforce the upper frame and the lower frame in a bracing manner.

Further, the first bearing or the second bearing tilts toward the worm part on the surface of the worm part side of at least one of the frame part, the first bearing, and the second bearing. By forming the rib portion that prevents this, the load applied to the worm portion due to the pinching of the bearing can be further reduced.

In addition, a grip portion made of a plane is formed on the surface opposite to the surface supporting the worm portion of at least one of the first bearing and the second bearing, so that the bearing can be held with a finger. Since it becomes easy to hold and it is possible to perform the attachment work efficiently with a light force, the force applied to the worm portion can be further reduced.

In addition, an insertion portion which is one or a plurality of convex portions protruding toward the case half body is formed on a joint surface of at least one of the first bearing and the second bearing with the case half body. In addition, an introduction portion having a smaller diameter than the root portion is formed at at least one tip portion of the fitting portion, and the introduction portion has a convex portion whose diameter is reduced perpendicularly to the axial direction or an axial length of the root portion. Because it is a taper-shaped convex part whose diameter becomes longer toward the case half body side than the part, it becomes easy to position the case half body, and it becomes possible to press-fit with a smaller pressing force, The force applied to the worm portion can be further reduced. Specifically, fitting portions that are a plurality of convex portions protruding toward the case half are formed on the joint surfaces of the first bearing and the second bearing with the case half. The leading portion of each of the insertion portions may be formed with the introduction portion. In this case, the plurality of insertion portions provided in the first bearing and the second bearing If the plurality of provided insertion portions are arranged in a direction orthogonal to the axial direction of the worm portion, the attachment to the case half is also stable.

The motor unit according to the present invention can prevent the worm part from being damaged or deformed even when the load applying means is manually attached.

It is the figure which showed the whole motor unit (state which removed the case) concerning this embodiment. It is a system diagram for demonstrating the power system of the motor unit concerning this embodiment. It is explanatory drawing of the gear mechanism which transmits motor motive power to a to-be-driven body. It is a front view which shows the engagement mechanism of two rotor gears. It is a disassembled perspective view of the differential gear mechanism which is a clutch means. It is a top view which shows the member which comprises a shift means. It is a front view which shows the biasing mechanism of a 2nd gearwheel and a lock lever. It is a perspective view which shows the bottom face of a sector lever. It is a perspective view of the load provision means of patent document 1. FIG. It is the perspective view (a) and exploded view (b) of the load provision means concerning this embodiment.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In addition, the upper and lower in the following description shall mean the upper and lower in FIG. The “original position” refers to the position of each constituent member in a state where the motor 10 is not driven.

Before describing each configuration of the motor unit 1 according to the present embodiment, the outline of the motor unit 1 will be briefly described with reference to the system diagram of FIG. As shown in FIG. 2, the power system of the motor unit 1 includes an output system (first transmission train) that transmits the power of the motor 10 to the driven body 90, and a clutch operation system (second transmission system) that operates the clutch means 30. Transmission train). The clutch means 30 switches the transmission of power by the output system to the “joining” state or the “disconnected” state. That is, if the clutch means 30 is in the “joined” state, the power of the motor 10 is transmitted to the driven body 90 through the output system. If the clutch means 30 is in the “disconnected” state, the output system is disconnected, and the power of the motor 10 is not transmitted to the driven body 90. As shown in the figure, in this embodiment, the driven body is used as the power of the clutch operating system for operating the clutch means 30 in this way (the power transmission by the first transmission train is set to the “joining” state). A part of the power of the motor 10 for driving 90 is used.

(Loading means)
With reference to FIG. 10, the structure of the load provision means 50 in this embodiment is demonstrated in detail.

The load application means 50 in this embodiment includes a worm portion 51 that meshes with a driven side tooth portion 442 that is a worm wheel portion of a second gear 44 described later, and a first bearing 53 that rotatably supports the worm portion 51. And a second bearing 54, a frame portion 55 that connects the first bearing 53 and the second bearing 54, and a load portion 52 that is a centrifugal brake that provides resistance to rotation of the worm portion 51.

The frame portion 55 is formed integrally with the second bearing 54 and is formed separately from the first bearing 53. The first bearing 53 is formed with a drum 531 for storing the load portion 52. The upper frame 551 that is the upper end portion of the frame portion 55 is located above the worm portion 51, and is formed in parallel with the worm portion 51 at a position above the worm portion 51. 54 is connected. A convex portion 5511 and a convex portion 5521 projecting toward the first bearing 53 are formed on the joint surface of the upper frame 551 and the lower frame 552, which is the opposite end thereof, with the first bearing 53. Are respectively fitted into a recess 532 and a recess 533 formed on the first bearing 53 side, whereby the frame portion 55 and the first bearing 53 are connected. The lower frame 552 is formed to connect the first bearing 53 and the second bearing 54 in parallel with the worm portion 51 at a position below the worm portion 51. Here, by narrowing the clearances of the concave portion 532 and the concave portion 533, the movable range of the first bearing 53 connected to the frame portion 55 is narrowed, and the rigidity against the tilt of the first bearing 53 toward the worm portion 51 is increased. be able to.

The frame portion 55 has a reinforcing portion 553 between the upper frame 551 and the lower frame 552, and the reinforcing portion 553 is provided with a through hole 5531 and is formed in a brace shape. By forming the reinforcing portion 553 in a brace shape, the frame portion 55 maintains the rigidity against the load applied from the vertical direction and the axial direction of the worm portion 51, while preventing the occurrence of sink marks and linearly forming without distortion. Is possible. However, the reinforcing portion 553 does not necessarily have a bracing shape, and it is sufficient if the concave portion and the through hole are formed to such an extent that sink marks can be prevented.

A rib portion 57 that prevents the second bearing 54 from tilting toward the worm portion 51 is formed on the surface of the frame portion 55 and the second bearing 54 on the worm portion 51 side. Such a rib may be formed at a position that prevents the first bearing 53 from tilting toward the worm portion 51, and may naturally be formed on both.

On the back surface of the second bearing 54, a grip portion 541 made of a flat surface is formed so that the operator can stably hold the load applying member 50 with a light force. The back surface of the first bearing 53 has a substantially flat surface.

The bottom surfaces of the first bearing 53 and the second bearing 54 are each provided with a plurality of insertion portions 56 that are convex portions protruding toward the lower case 82 that is the case half, and at the tip of the insertion portion 56 An introduction portion having a smaller diameter than the root portion is formed, and these introduction portions are convex portions whose diameters are reduced perpendicularly to the axial direction, or the axial length is longer than the root portion and the diameter thereof toward the lower case 82 side. Since it becomes the taper-shaped convex part which becomes small, the positioning at the time of attaching the load provision member 50 to the lower case 82 becomes easy, and it can be press-fitted with a small pressing force. A plurality of insertion portions 56 are provided on the bottom surfaces of the first bearing 53 and the second bearing 54, and a plurality of insertion portions 56 provided on the bottom surface of the first bearing 53 and a bottom surface of the second bearing 54 are provided. Since the plurality of fitting portions 56 are arranged in a direction orthogonal to the axial direction of the worm portion 51, the load applying member 50 can be attached to the lower case 82 together with the second bearing 54 in a stable state. it can.

The load applying means 50 in the present embodiment has the above-described configurations, so that when the operator attaches the load applying means 50 to the lower case 82, the back surfaces of the first bearing 53 and the second bearing 54 are held by fingers. The load to be applied reaches the worm portion 51, and the worm portion 51 is prevented from being damaged or deformed.

(Motor 10)
The motor 10 that is a drive source of the driven body 90 is an AC synchronous motor. A motor other than the AC synchronous motor can also be applied. The motor 10 has a rotating shaft that protrudes from its upper end surface.

(First transmission line)
Hereinafter, the first transmission train will be described in detail with reference to FIGS. The first transmission train constitutes an output system that transmits the power of the synchronous motor 10 to the driven body 90. The first transmission train includes the second rotor gear 21, the input side gear 22 meshing with the second rotor gear 21, and the rotation of the input side gear 22 when the clutch means is in the "joint" state. The output side gear 23 that rotates, the composite gear 24 that meshes with the output side gear 23, the cam gear 25 that meshes with the composite gear 24, the pulley 26 that rotates integrally with the cam gear 25, and the pulley 26 is wound up by rotation. Wire 27 to be provided. The input side gear 22 and the output side gear 23 are also gears constituting clutch means (differential gear mechanism based on a planetary gear train) whose details will be described later.

The second rotor gear 21 is a spur gear supported so as to be rotatable on the same axis as the synchronous motor 10 and movable in the axial direction. The second rotor gear 21 is arranged on the first rotor gear 41 rotating integrally with the rotor 11 (rotation). It is supported on the tip side of the shaft. The second rotor gear 21 is urged upward in the axial direction by a coil spring 28. On the lower surface of the second rotor gear 21, an upper engagement portion 212 that engages with the lower engagement portion 412 of the first rotor gear 41 when the second rotor gear 21 is positioned on the rotor 11 side (lower side). Is formed. The position of the second rotor gear 21 in a state where the lower engagement portion 412 and the upper engagement portion 212 are engaged is referred to as a first position. The position of the second rotor gear 21 in a state where the lower engagement portion 412 and the upper engagement portion 212 are not engaged is referred to as a second position.

The second rotor gear 21 is moved to the rotor 11 side by an inclined cam 63 (see FIG. 8) of the sector lever 60 described later, and the second rotor gear 21 has an upper engagement portion 212 and a first rotor gear 41 below. When the engaging portion 412 is engaged (the second rotor gear 21 is in the first position), the second rotor gear 21 and the first rotor gear 41 rotate integrally. That is, the power of the synchronous motor 10 is also transmitted to the second rotor gear 21.

The input side gear 22 meshes with the second rotor gear 21. The input side gear 22 is one gear constituting a planetary gear train. The input side gear 22 has a relatively large diameter large diameter tooth portion 221 and a relatively small diameter small diameter tooth portion 222 which is a so-called sun gear. The large-diameter tooth portion 221 of the input side gear 22 meshes with the second rotor gear 21, and the input side gear 22 rotates as the second rotor gear 21 rotates. Further, a locked projection 223 is formed on the upper surface of the input side gear 22. An input side gear lock projection 62 of the sector lever 60 described later acts on the locked projection 223.

The power of the synchronous motor 10 is transmitted to the output side gear 23 via the second rotor gear 21. The output side gear 23 in this embodiment corresponds to the three planetary gears 231 and the planetary support gear 232 that are gears constituting the planetary gear train. The planetary gears 231 are rotatably supported on three planetary gear support shafts that protrude from the upper end surface of the planetary support gear 232 and are provided at equal intervals in the circumferential direction. A retaining ring 233 is fixed to the upper end of the planetary gear support shaft to prevent the planetary gear 231 from falling off. The planetary support gear 232 has a gear portion 2321 on the side opposite to the surface to which the planetary gear 231 is attached. The planetary gear 231 meshes with the small diameter tooth portion 222 of the input side gear 22. Although details will be described later, when the clutch means is in the “joining” state, the planetary gear 231 revolves around the small-diameter tooth portion 222 of the input side gear 22 as the input side gear 22 rotates. With the revolution of the planetary gear 231, the planetary support gear 232 that supports the planetary gear 231 rotates. In this way, power is transmitted from the input side gear 22 to the output side gear 23.

The compound gear 24 meshes with the planetary support gear 232 (output side gear 23). The compound gear 24 has a relatively small diameter tooth portion 241 and a relatively large diameter tooth portion 242, and the large diameter tooth portion 242 meshes with the gear portion 2321 of the planetary support gear 232. . As a result, the compound gear 24 rotates as the planetary support gear 232 rotates.

The cam gear 25 meshes with the compound gear 24. A gear portion 251 of the cam gear 25 meshes with a small diameter tooth portion 241 of the compound gear 24. As a result, the cam gear 25 rotates as the compound gear 24 rotates. A cam groove 252 is formed on the upper end surface of the portion where the gear portion 251 is formed on the outer periphery. A fan-shaped lever 60 described later is engaged with the cam groove 252. The configuration and operation of the sector lever 60 will be described later.

A pulley 26 is fixed to the cam gear 25. The fixing method is not particularly limited as long as the pulley 26 rotates integrally with the cam gear 25. Thereby, the pulley 26 rotates with the rotation of the cam gear 25. The pulley 26 is exposed outside the case. A wire groove 261 is formed on the outer periphery of the pulley 26.

One end of a wire 27 is fixed to the pulley 26. The fixing method is not particularly limited as long as it can reliably prevent the wire 27 from falling off. When the pulley 26 rotates in the direction in which the wire 27 is drawn, the wire 27 is wound up so as to fit into the wire groove 261 of the pulley 26. A driven body 90 (for example, a valve body that opens and closes the drain port) is fixed to the other end side of the wire 27, and the driven body 90 is always returned to the original position (position where the valve body is closed). A load in the direction of pulling out, that is, the direction of pulling out the wire 27 is acting. When the wire 27 is wound around the pulley 26, the driven body 90 performs a predetermined operation. That is, when the wire 27 is wound around the pulley 26, the power of the synchronous motor 10 is transmitted to the driven body 90 via the first transmission train. In addition, in order to operate the driven body 90 accurately, the wire 27 is formed of a non-stretchable material.

(Clutch means)
Hereinafter, the clutch means will be described in detail with reference to FIG. The clutch means plays a role of switching the power transmission (output system) by the first transmission train to the “joining” state or the “disconnection” state. The operation of the clutch means in the present embodiment includes the input side gear 22 (small gear tooth portion 222 that is a sun gear), the output side gear 23 (the planetary gear 231 and the planetary support gear 232), and the fixed gear 31 (ring gear). The differential gear mechanism based on the planetary gear train is used.

As already described, the input side gear 22 meshes with the second rotor gear 21 and rotates as the second rotor gear 21 rotates. Three planetary gears 231 arranged at equal intervals in the circumferential direction mesh with the small-diameter tooth portion 222 of the input side gear 22. The planetary gear 231 is supported on the planetary support gear 232. The planetary support gear 232 rotates with the revolution of the planetary gear 231.

The fixed gear 31 that is a ring gear constituting the planetary gear train has an outer tooth portion 311 and an inner tooth portion 312. The external tooth portion 311 of the fixed gear 31 is located below the large-diameter tooth portion 221 of the input side gear 22 and meshes with a lock gear 47 that is one gear constituting a second transmission train described later. . That is, when the rotation of the lock gear 47 is blocked, the rotation of the fixed gear 31 is blocked. The internal gear portion 312 of the fixed gear 31 meshes with the three planetary gears 231.

In the clutch means having such a configuration, whether or not the planetary gear 231 revolves and the planetary support gear 232 rotates depends on whether or not the rotation of the fixed gear 31 is blocked.
In the case where the rotation of the fixed gear 31 is blocked, when the input side gear 22 rotates, the internal tooth portion 312 of the fixed gear 31 does not move. Therefore, the small diameter tooth of the input side gear 22 along the internal tooth portion 312. The planetary gear 231 meshing with the portion 222 revolves and the planetary support gear 232 rotates. On the other hand, when the rotation of the fixed gear 31 is not blocked, even if the input side gear 22 rotates and the planetary gear 231 tries to revolve, the fixed gear 31 rotates idly, so that the planetary support gear 232 does not rotate.

That is, if the rotation of the fixed gear 31 is prevented, the first transmission train is in the “join” state, and if the rotation of the fixed gear 31 is not blocked, the first transmission train is in the “disconnected” state. . If the first transmission train is in the “joining” state by the clutch means, that is, if the output system is in the “joining” state, the power of the synchronous motor 10 is transmitted to the driven body 90 via the first transmission train. On the other hand, if the first transmission train is in the “disconnected” state by the clutch means, that is, if the output system is in the “disconnected” state, the power of the synchronous motor 10 is disconnected by the clutch means (the input gear 22 and the output gear 23 are And is not transmitted to the driven body 90.

(Second transmission line)
Hereinafter, the second transmission train will be described in detail with reference to FIGS. The second transmission train constitutes a clutch operating system that transmits the power of the synchronous motor 10 to the clutch means. The second transmission train includes a first rotor gear 41, a first gear 42 meshing with the first rotor gear 41, a second gear 44 meshing with the first gear 42, and a second gear. It has a lock lever 45 that is pushed down when 44 moves downward in the axial direction, and a lock gear 47 that is locked by the pushed down lock lever 45.

The first rotor gear 41 is a spur gear formed integrally with the rotor 11 of the synchronous motor 10. It is provided under the second rotor gear 21 described above (on the main body side of the synchronous motor 10).

A first gear 42 meshes with the first rotor gear 41. It has a driving side tooth part 421 and a first helical tooth part 422 having a relatively smaller diameter than the driving side tooth part 421. The first helical tooth portion 422 is a portion formed into a “helical tooth” as described above. The first gear 42 has a drive-side tooth portion 421 meshed with the first rotor gear 41. Therefore, the first gear 42 rotates as the first rotor gear 41 rotates.

The second gear 44 meshes with the first gear 42. The second gear 44 includes a second helical tooth portion 441 having a relatively large diameter and a driven side tooth portion 442 having a relatively small diameter. The second gear 44 is supported by the second gear support shaft 86 so as to be rotatable and movable in the axial direction. As described above, the second helical tooth portion 441 is a portion formed into a “helical tooth”. The driven side tooth portion 442 is a so-called worm wheel portion that meshes with the worm portion 51 included in the load applying means 50. The driven tooth portion 442 may be a helical tooth or a spur gear.

In the second gear 44, the second helical tooth portion 441 is engaged with the first helical tooth portion 422 of the first gear 42. Therefore, the second gear 44 rotates as the first gear 42 rotates. When the synchronous motor 10 rotates in the forward direction, a load in the direction opposite to the rotation direction is applied to the second gear 44 by the load applying means 50, so that a downward thrust force in the axial direction is generated. Therefore, when the first gear 42 rotates, the second gear 44 moves downward in the axial direction while rotating.

The lock lever 45 is a flat member and is disposed under the second gear 44. Specifically, it is supported by a second gear support shaft 86 that is the same as the second gear 44 and is movable in the axial direction. A recess 452 is formed in the lock lever 45, and the recess 452 is engaged with a not-shown protrusion formed along the axial direction inside the side wall of the lower case 82. Due to the engagement between the convex portion and the concave portion 452, the lock lever 45 is supported by the second gear support shaft 86 while being prevented from rotating and movable in the axial direction. At one end portion of the lock lever 45, a lock portion 451 is formed that is thicker than the other portions. A biasing member 46 (coil spring) that biases the lock lever 45 upward is disposed below the lock lever 45. Due to the urging member 46, the lock lever 45 is positioned above the locked portion 471 of the lock gear 47 during normal times (when the synchronous motor 10 is not driven). Further, since the second gear 44 is disposed on the lock lever 45, the second gear 44 is also urged upward in the axial direction. The urging force of the urging member 46 is smaller than the axially downward thrust force generated in the second gear 44 when the second gear 44 rotates as the first gear 42 rotates. That is, when the second gear 44 rotates, the second gear 44 moves downward in the axial direction against the biasing force of the biasing member 46. When the second gear 44 moves downward in the axial direction, the lock lever 45 underneath also moves downward. The lock portion 451 of the lock lever 45 moved downward is positioned at substantially the same height as the locked portion 471 of the lock gear 47.

The lock gear 47 includes a locked portion 471 and a lock tooth portion 472 on a flat plate on which the locked portion 471 is formed. The locked portion 471 is formed so as to protrude outward from the circular flat plate. When the lock lever 45 moves downward, the lock portion 451 of the lock lever 45 and the locked portion 471 of the lock gear 47 are positioned so as to face each other, so that the rotation of the lock gear 47 is at a predetermined position (the lock portion 451 and the locked portion). At a position where the 471 is in contact). On the other hand, the lock tooth portion 472 meshes with the external tooth portion 311 of the fixed gear 31 constituting the clutch means. Accordingly, when the rotation of the lock gear 47 is blocked, the rotation of the fixed gear 31 meshing with the lock gear 47 is also blocked. In the present embodiment, the lock gear 47 has a brake portion 473 that is a centrifugal brake. The brake unit 473 applies a load in a direction that prevents the lock gear 47 from rotating, and prevents the lock gear 47 from rotating at a higher speed than necessary.
The effect | action of this brake part 473 is mentioned later.

The worm part 51 extending in the direction orthogonal to the axial direction of the second gear 44 meshes with the driven side tooth part 442 (worm wheel part). The worm part 51 is one line, and the driven side tooth part 442 and the worm part 51 constitute a speed increasing gear mechanism (when the driven side tooth part 442 rotates by one tooth, the worm part 51 makes one rotation). Therefore, the rotation of the second gear 44 is increased and transmitted to the worm portion 51.

(Other configurations)
As shown in FIGS. 1 and 8, a sector lever 60 is arranged on the compound gear 24. The sector lever 60 is rotatably supported on the same shaft as the shaft on which the compound gear 24 is rotatably supported. An engaging protrusion 61 is formed on the lower surface of the sector lever 60. The engaging protrusion 61 is engaged with a cam groove 252 formed on the upper surface of the cam gear 25. Similarly, the sector lever 60 is formed with an input side gear lock projection 62 and an inclined cam 63. Although details of the engagement protrusion 61, the cam groove 252, the input side gear lock protrusion 62, and the inclined cam 63 are omitted, the function of each member is as follows. When the cam gear 25 rotates in the direction in which the wire 27 is wound up, the sector lever 60 is rotated toward the input side gear 22 by the engagement protrusion 61 that engages with the cam groove 252. When the sector lever 60 moves to a predetermined position (the wire 27 is wound up to a predetermined position), the input side gear lock projection 62 acts on the locked projection 223 of the input side gear 22 to stop the winding of the wire 27, and the input side The rotation of the gear 22 is prevented.
At the same time, the second rotor gear 21 pressed downward in the axial direction by the inclined cam 63 is released and moved upward in the axial direction by the coil spring 28 (the second rotor gear 21 is positioned at the second position). (See FIG. 4). As a result, the engagement between the upper engagement portion 212 of the second rotor gear 21 and the lower engagement portion 412 of the first rotor gear 41 is released. That is, the power of the synchronous motor 10 is not transmitted to the second rotor gear 21.

(Operation of motor unit)
The normal operation of the motor unit 1 having the above configuration will be described in detail below. In the following description, the power of the synchronous motor 10 is transmitted to the driven body 90 in the original position. ) The explanation will be divided into the power cut-off operation.

1) Power transmission operation Synchronous motor from a state where the driven body 90 is in the original position (a state where the wire 27 is not wound around the pulley 26, that is, a state where the power of the synchronous motor 10 does not act on the driven body 90) When 10 is driven in one direction (forward rotation), the second rotor gear 21 and the first rotor gear 41 rotate. At this time, when the synchronous motor 10 rotates in the reverse direction, a reverse rotation prevention mechanism (not shown) works, and the synchronous motor 10 immediately rotates forward. When the synchronous motor 10 is driven, the rotation of the first rotor gear 41 causes the first gear 42 having the drive-side tooth portion 421 that meshes with the first rotor gear 41 to rotate.

When the first gear 42 rotates, the second gear 44 having the second helical gear portion 441 that meshes with the first helical gear portion 422 of the first gear 42 rotates. The second gear 44 has a driven side tooth portion 442 (worm wheel portion) meshed with the worm portion 51 of the load applying means 50, and the load portion of the load applying means 50 is rotated by the rotation of the second gear 44. 52 also rotates. When the load unit 52 rotates and its speed increases, a load (torque) is generated in a direction in which the rotation is stopped. The load is transmitted from the worm portion 51 to the second gear 44 having the driven side tooth portion 442 and the first gear 42 meshing with the second gear 44. In this way, the first gear 42 and the second gear 44 are subjected to loads opposite to their rotational directions.

As described above, the transmission of power between the first gear 42 and the second gear 44 is based on meshing of “helical teeth”. Therefore, the second gear 44 that has received a load opposite to the rotation direction from the load applying means 50 receives a downward thrust force in the axial direction due to the rotation of the first gear 42. In other words, the second gear 44 moves downward in the axial direction while rotating by a load opposite to the meshing of the “helical teeth” and the rotation direction.

In the present embodiment, since the meshing between the second gear 44 and the load applying means 50 is also based on “helical teeth”, a large axial downward thrust force is generated with respect to the second gear 44.
That is, the load generated by the load portion 52 is transmitted to the second gear 44 by meshing between the worm portion 51 and the driven side tooth portion 442, and therefore the axial downward thrust force due to the transmission of the load is also the second. Is generated in the gear 44.

When the second gear 44 moves downward in the axial direction, the lock lever 45 disposed under the second gear 44 moves downward in the axial direction against the biasing force of the biasing member 46. When the lock lever 45 is pushed down in this way, the lock portion 451 provided on the lock lever 45 is substantially the same height as the locked portion 471 of the lock gear 47 and faces the lock gear 47 in the circumferential direction. To position. Accordingly, in this state, the rotation of the lock gear 47 is prevented by the lock portion 451 of the lock lever 45. That is, the lock gear 47 is prevented from rotating.

The lock gear 47 has its lock tooth portion 472 meshed with the external tooth portion 311 of the fixed gear 31 constituting the planetary gear train of the clutch means. Therefore, when the rotation of the lock gear 47 is blocked, the rotation of the fixed gear 31 is also blocked. As a result, the transmission of power by the first transmission train by the clutch means is in the “joint” state, and the power of the synchronous motor 10 can be transmitted to the driven body 90 through the first transmission train. In this way, the second gear 44 moves downward in the axial direction thereof, thereby bringing the power transmission by the first transmission train into the “joining” state via the clutch means.

On the other hand, the second rotor gear 21 that rotates together with the first rotor gear 41 by driving the synchronous motor 10 meshes with the large-diameter tooth portion 221 of the input-side gear 22 that constitutes the planetary gear train. Accordingly, the input side gear 22 rotates with the rotation of the second rotor gear 21.

The three planetary gears 231 constituting the output side gear 23 are meshed with the outside of the small-diameter tooth portion 222 of the input side gear 22. An inner tooth portion 312 of the fixed gear 31 meshes with the outside of the planetary gears 231 arranged at equal intervals in the circumferential direction. As described above, the fixed gear 31 is prevented from rotating by the lock gear 47. Therefore, when the input side gear 22 rotates, the planetary gear 231 revolves around the small diameter tooth portion 222. When the planetary gear 231 revolves, the planetary support gear 232 that supports the planetary gear 231 rotates. That is, all the rotational power of the input side gear 22 is transmitted to the output side gear 23.

If the input side gear 22 rotates when the rotation of the fixed gear 31 is not blocked, the fixed gear 31 rotates idle via the planetary gear 231. Since the power transmission train after the planetary support gear 232 includes a load on the transmission train itself and a load on the driven body 90, all the rotational power of the input side gear 22 is transmitted to the fixed gear 31 side. It is. As described above, in the present embodiment, the “transmission” state and the “disconnection” state of the first transmission train by the clutch means are switched by the differential gear mechanism using the planetary gear train.

The large-diameter tooth portion 242 of the compound gear 24 meshes with the gear portion 2321 of the planetary support gear 232. Therefore, the compound gear 24 rotates as the planetary support gear 232 rotates.

The gear portion 251 of the cam gear 25 meshes with the small diameter tooth portion 241 of the composite gear 24. Therefore, the cam gear 25 rotates with the rotation of the compound gear 24.

When the cam gear 25 rotates, the pulley 26 fixed to the upper end of the cam gear 25 rotates.
When the pulley 26 rotates, the wire 27 fixed to the pulley 26 is wound up along the wire groove 261. Since the driven body 90 is fixed to the tip of the wire 27, the driven body 90 operates to be pulled up by the wire 27. For example, when the driven body 90 is a valve body that opens and closes the drain port of the washing machine, the valve body is pulled up by the wire 27 so that the drain port is opened and drainage is started.

Thus, the rotational power of the synchronous motor 10 is transmitted to the driven body 90 via the first transmission train. The first transmission train is put into the “engaged” state by the clutch means, but a part of the rotational power of the synchronous motor 10 is also used for the power to put the clutch means in the “joined” state.

The winding of the wire 27 by the pulley 26 is stopped as follows. When the cam gear 25 rotates to a predetermined position (when the wire 27 is wound up by a predetermined amount), the sector lever 60 having the engaging protrusion 61 that engages with the cam groove 252 rotates toward the input side gear 22. When the sector lever 60 rotates in this manner, the input side gear lock protrusion 62 of the sector lever 60 contacts the locked protrusion 223 of the input side gear 22 from the circumferential direction. As a result, the input side gear 22 is prevented from rotating. Further, the second rotor gear 21 pressed downward in the axial direction by the inclined cam 63 of the sector lever 60 is released and moved upward in the axial direction by the coil spring (the second rotor gear 21 is moved to the second position). To position). As a result, the upper engagement portion 212 of the second rotor gear 21 and the lower engagement portion 412 of the first rotor gear 41 are disengaged, and the power of the synchronous motor 10 is transmitted to the second rotor gear 21. It will be in a state that is not.
When the rotation of the input side gear 22 stops, the operation of each member constituting the first transmission train also stops.
That is, the winding of the wire 27 by the pulley 26 is stopped, and the pulley 26 is held at the winding position (when the driven body 90 is a valve body that opens and closes the drain of the washing machine, the drain is opened). Is maintained). Thus, in the state where the drain opening is maintained, the synchronous motor 10 continues to be driven, but the power is not transmitted to the second rotor gear 21 (first transmission train). Therefore, the load applied to the synchronous motor 10 is small, and the power consumption can be reduced.

In this way, the power transmission operation for transmitting the power of the synchronous motor 10 to the driven body 90 is completed.

2) Power cut-off operation When the driven body 90 is returned to the original position after the power transmission operation is completed, the drive of the synchronous motor 10 is stopped (the energization to the synchronous motor 10 is stopped). Then, since the rotation of the first rotor gear 41 and the first gear 42 is stopped, the rotation of the second gear 44 is also stopped. When the rotation of the second gear 44 is stopped, the axial downward thrust force with respect to the second gear 44 generated by the engagement of the “helical teeth” and the load applied by the load applying means 50 disappears. Since the second gear 44 is urged upward in the axial direction by the urging member 46 together with the lock lever 45 arranged thereunder, the second gear 44 rotates while the second gear 44 rotates in the axial direction. Move upward and return to the original position. Of course, the lock lever 45 also moves in this direction and returns to the original position. Since the force of the urging member 46 to return the second gear 44 to the original position is small, the rotation speed of the second gear 44 and the load portion 52 is low, and the weight of the load portion 52 contacts the drum 531. do not do. Therefore, the magnitude of the load acting on the second gear 44 by the load applying means 50 does not increase, and the second gear 44 returns smoothly to the original position.

When the lock lever 45 is moved upward by the urging member 46, the height direction position of the lock portion 451 of the lock lever 45 becomes higher than the height direction position of the locked portion 471 of the lock gear 47. Specifically, the lock portion 451 and the locked portion 471 are positioned so as not to overlap in the circumferential direction. Therefore, the state in which the rotation of the lock gear 47 is prevented is eliminated, and the lock gear 47 can be freely rotated. That is, the fixed gear 31 of the clutch means (planetary gear train) can freely rotate, that is, the clutch means is in the “disengaged” state. In this way, the second gear 44 moves upward in the axial direction thereof, thereby bringing the power transmission by the first transmission train into the “disconnected” state via the clutch means.

The driven body 90 is always going to return to its original position by an external load acting on itself. For example, when the driven body 90 is a valve body that opens and closes a drain port of a washing machine, and the valve body is operated in a direction to open the drain port by driving the motor unit 1, the valve body always opens the drain port. It is biased in the closing direction. Therefore, when the clutch means that can freely rotate the fixed gear 31 is in the “disengaged” state, the load applied to the driven body 90 reverses the first transmission train so that the output side gear 23 (planet support) To the gear 232). The energy based on the load applied to the driven body 90 thus transmitted is output (consumed) by the idling of the output side gear 23 because the clutch means is in the “disengaged” state. Thereby, the driven body 90 returns to the original position.

Further, when the cam gear 25 returns to the original position, the sector lever 60 having the engaging protrusion 61 that engages with the cam groove 252 rotates in a direction approaching the cam gear 25. When the sector lever 60 rotates in this way, the input side gear lock projection 62 of the sector lever 60 is separated from the locked projection 223 of the input side gear 22. As a result, the input side gear 22 is allowed to rotate. Further, the second rotor gear 21 urged upward in the axial direction by the coil spring is pressed against the inclined cam 63 and moves downward in the axial direction (the second rotor gear 21 is located at the first position). ). As a result, the upper engagement portion 212 of the second rotor gear 21 and the lower engagement portion 412 of the first rotor gear 41 are engaged, and the power of the synchronous motor 10 is also transmitted to the second rotor gear 21. It becomes a state.

At this time, the brake portion 473 of the lock gear 47 brakes the operation of the driven body 90 to return to the original position, and softens the impact applied to the first transmission train. Therefore, it is possible to prevent damage to the power transmission member, which is an individual member constituting the first transmission train. In addition, when the driven body 90 returns to the original position, an impact sound that collides with each other (when the driven body 90 is a valve body that opens and closes the drain port of the washing machine, the valve body is connected to the drain port. (Impact sound that collides with the surroundings) can be reduced.

Thus, when the synchronous motor 10 is stopped, the locking of the fixed gear 31 constituting the planetary gear train is released by the action of the urging member 46, and the clutch means places the first transmission train in the “disconnected” state. Thereby, the driven body 90 returns to the original position.

The embodiments of the present invention have been described in detail above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the present invention.

DESCRIPTION OF SYMBOLS 1 Motor unit 10 Synchronous motor 21 Second rotor gear 41 First rotor gear 22 Input side gear 23 Output side gear 231 Planetary gear 24 Compound gear 25 Cam gear 42 First gear 44 Second gear 45 Lock lever 47 Lock Gear 50 Load applying means 60 Fan lever

Claims

A motor that rotates in one direction;
A first transmission train having one or more power transmission members for transmitting the power of the motor to a driven body;
Clutch means for switching the transmission of power by the first transmission train to a "continuous" state or a "disconnected"state;
A transmission train for transmitting the power of the motor to the clutch means, a first gear having a first helical tooth portion, and a second helical gear portion meshing with the first tooth portion. A second transmission train having a second gear formed with
Load applying means for applying a load to the rotation of the second gear,
The second gear is supported so as to be movable in the axial direction, and is constantly urged in one direction of the axial direction so that the clutch means is in a “disengaged” state, and meshes with the first gear. A motor unit that moves to the other side in the axial direction against the urging force by a thrust force generated by applying a load from the load applying unit, and puts the clutch unit in a “joining” state;
A worm wheel portion is formed on the second gear,
The load applying means includes a worm portion that meshes with the worm wheel portion, a first bearing and a second bearing that rotatably support the worm portion, and the first bearing and the second bearing. A frame portion to be connected; and a brake portion that provides resistance to rotation of the worm portion;
The upper frame, which is the upper end portion of the frame portion, is located above the support position of the worm portion with the joint surface side to the case half of the load applying means facing down, and the first bearing and the second bearing And a motor unit characterized by being connected to each other.
The said frame part connects said 1st bearing and said 2nd bearing by the lower frame which is the upper frame and the other side edge part of the said upper frame, The said 2nd bearing is characterized by the above-mentioned. Motor unit.
At least one of the first bearing and the second bearing is molded separately from the frame part,
On the joint surface of the lower frame, which is the opposite end portion of the upper frame and the upper frame, with the separately molded bearing, a convex portion protruding to the separately molded bearing side is formed. The frame portion and the separately molded bearing are connected by fitting the convex portion with a concave portion formed in the separately molded bearing. The motor unit according to 1.
The said frame part has a reinforcement part between the said upper frame and the said lower frame, The recessed part or the through-hole is formed in this reinforcement part, The Claim 2 or Claim 3 characterized by the above-mentioned. Motor unit.
The first bearing or the second bearing tilts toward the worm portion on the surface on the worm portion side of at least one of the frame portion, the first bearing, and the second bearing. The motor unit according to any one of claims 1 to 4, wherein a rib portion is provided to prevent the above.
The grip part which consists of a plane is formed in the surface on the opposite side to the surface which supports the said worm | warm part of at least one among said 1st bearing and said 2nd bearing. The motor unit according to claim 5.
In the joint surface with the case half of at least one of the first bearing and the second bearing, a fitting portion that is one or a plurality of protrusions protruding toward the case half is formed.
An introduction portion having a smaller diameter than the root portion is formed at at least one tip portion of the fitting portion, and the introduction portion has a convex portion whose diameter is reduced perpendicularly to the axial direction, or an axial length of the root portion. The motor unit according to any one of claims 1 to 6, wherein the motor unit is a taper-shaped convex portion that has a longer diameter toward the case half side.
The upper frame is formed to connect the first bearing and the second bearing in parallel with the worm portion at a position above the worm portion,
The lower frame is formed to connect the first bearing and the second bearing in parallel to the worm portion at a position below the worm portion,
The motor unit according to claim 2, wherein the upper frame and the lower frame are connected to each other via a reinforcing portion having a recess or a through hole between the upper frame and the lower frame.
The motor unit according to claim 8, wherein the reinforcing portion is provided with the through hole so as to reinforce the upper frame and the lower frame in a bracing manner.
The frame portion is integrally molded with the second bearing, and the first bearing is formed with a drum for storing the brake portion,
On the joint surface of the upper frame and the lower frame with the first bearing, a convex portion protruding to the first bearing side is formed, and the convex portion is formed on the first bearing side. 4. The motor unit according to claim 3, wherein the frame portion and the first bearing are coupled by being respectively fitted in the recess.
The rib portion for preventing the second bearing from tilting toward the worm portion side is formed on a surface of the lower frame and the second bearing on the worm portion side. The motor unit according to 10.
The frame part is integrally molded with the second bearing, and the first bearing is provided with a drum for storing the brake part,
The rib portion for preventing the second bearing from tilting toward the worm portion side is formed on a surface of the frame portion and the second bearing on the worm portion side. 5. The motor unit according to 5.
In the frame portion, the first bearing and the second bearing are connected by the upper frame and a lower frame which is an opposite end portion of the upper frame,
The upper frame is formed to connect the first bearing and the second bearing in parallel with the worm portion at a position above the worm portion,
The lower frame is formed to connect the first bearing and the second bearing in parallel to the worm portion at a position below the worm portion,
The motor unit according to claim 12, wherein the upper frame and the lower frame are connected via a reinforcing portion having a recess or a through hole between the upper frame and the lower frame.
In the frame portion, the first bearing and the second bearing are connected by the upper frame and a lower frame which is an opposite end portion of the upper frame,
The upper frame is formed to connect the first bearing and the second bearing in parallel with the worm portion at a position above the worm portion,
The lower frame is formed to connect the first bearing and the second bearing in parallel to the worm portion at a position below the worm portion,
The upper frame and the lower frame have the first bearing and the second bearing on the opposite side of the worm portion from the side where the worm wheel portion of the second gear is disposed. The motor unit according to claim 6, wherein the motor unit is connected.
In the joint surface of each of the first bearing and the second bearing with the case half, insertion portions that are a plurality of protrusions protruding toward the case half are formed.
The motor unit according to claim 7, wherein the introduction portion is formed at a distal end portion of each of the plurality of insertion portions.
The plurality of insertion portions provided in the first bearing and the plurality of insertion portions provided in the second bearing are arranged in a direction orthogonal to the axial direction of the worm portion. The motor unit according to claim 15, which is characterized by:
The upper frame is formed to connect the first bearing and the second bearing in parallel with the worm portion at a position above the worm portion,
The lower frame, which is the opposite end of the upper frame, is formed to connect the first bearing and the second bearing in parallel with the worm portion at a position below the worm portion. And
The motor unit according to claim 3, wherein the upper frame and the lower frame are connected to each other via a reinforcing portion having a recess or a through hole between the upper frame and the lower frame.
18. The motor unit according to claim 17, wherein the reinforcing portion is provided with the through hole so as to reinforce the upper frame and the lower frame in a bracing manner.