JPH0951654A - Driver for synchronous motor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent abnormal abrasion of a friction clutch by a structure wherein first and second rotators frictionally transmit the rotation of a rotor only in a predetermined direction and rotate integrally in case of reverse rota tion. SOLUTION: When a rotor 6 rotates in a predetermined direction, a first rotator 13 rotates in a predetermined direction. The rotation is transmitted through one way frictional rotation transmission mechanisms 14, 15, 16a to a second rotator 16 which is thereby rotated under no-load during a first idle interval. In this regard, the one way frictional rotation transmission mechanisms 14, 15, 16a do not rotate integrally but rotate frictionally and the second rotator 16 rotates, while sliding, in a predetermined direction with a lag behind the first rotator 13. This state is sustained until the rotor 6 is coupled with the second rotator 16. After being coupled with the second rotator 16, the rotor 6 sustains synchronous rotation.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive device that drives an external load using a synchronous motor as a drive source.

[0002]

2. Description of the Related Art Conventionally, a synchronous motor has been used as a drive source for driving an external load such as a fan blade. This is because a synchronous motor that uses a permanent magnet or the like as a rotor has higher efficiency, a simple structure, a smaller size, a lighter weight, and a lower cost compared to a Kumabe-coil induction motor, etc. This is because it has an advantage.
However, the synchronous motor has drawbacks that the rotation direction is undefined each time it is started and a separate rotation direction regulating lever is required, and that the starting torque is extremely small and the load cannot be started when the load is connected to the rotor shaft. are doing.

As one means for solving this drawback,
The technique of Japanese Examined Patent Publication No. 4-24943 is known. In this technology, a conical torsion spring is interposed between a fan boss and an output shaft that is rotatable with respect to the boss, and a clutch spring is wound around the boss. It can only be rotated in one direction. However, in order to start a fan with a large load, a high-output synchronous motor is required, and if the conical torsion spring is loosened so that a low-output synchronous motor can also be started, the output shaft and fan There is a problem that slip occurs even during synchronous rotation.

Therefore, as one means for solving this problem, the present applicant has applied for the technique of Japanese Patent Application No. 6-329792. As shown in FIGS. 13 and 14, this technique is configured such that a lever 62 that is swung by centrifugal force is interposed between the output shaft 53 and the impeller 60. That is, the synchronous motor includes the stator core 51, the rotor 52, the output shaft 53, the magnetic path piece 54 of the stator core 51, and the drive coil 5.
5, 55, bearings 56, 57 of the output shaft 53, these bearings 5
It is composed of a cylindrical case 58 that holds 6, 57.

A boss member 59 is fixed to the output shaft 53, and an impeller 60 is rotatably supported. A one-way clutch coil spring 61 is slidably attached to the boss member 59, and one end 61a thereof is
It is attached to the impeller 60. A lever 62 that is operated by centrifugal force is attached to the impeller 60 so as to swing about a pin 60a as a fulcrum. One end 63a of a coil spring 63 is attached to the lever 62, and the other end 63b of the coil spring 63 is attached to the boss portion 60 of the impeller 60.
It is attached to b and is urged so that the lever 62 contacts the boss portion 60b. The output shaft 53 has a lever 62
Is integrally attached to the engaging member 64, and engaging portions 64a, 64a to which the lever 62 receiving a centrifugal force is fitted are provided on the inner peripheral surface of the engaging member 64. A pump case 65 is attached so as to cover the impeller 60 and the like.

The drive coil 5 of the drive device having such a structure
When an alternating current is applied to 5, 55, the rotor 52 begins to oscillate left and right due to the alternating magnetic field, and the rotation causes the output shaft 53 to rotate. Then, the impeller 60 coupled to the output shaft 53 via the one-way clutch coil spring 61 tries to rotate. However, if the rotation direction is the winding tightening direction of the one-way clutch coil spring 61,
Since the impeller 60 and the output shaft 53 are directly connected to each other and the water load and the total load of the impeller 60 are applied to the rotor 52, the rotor 52 cannot be rotationally activated. On the other hand, when the rotation direction is the unwinding direction of the one-way clutch coil spring 61, the load of water and the total load of the impeller act in the direction of expanding the diameter of the coil spring 61, and the boss member 59 of the output shaft 53 is in the one direction. The direction clutch coil spring 61 slips, and the rotor 52 and the output shaft 53 continue to rotate. In this way, unidirectional rotation of the output shaft 53 and the rotor 52 is achieved.

When the output shaft 53 starts to rotate, the impeller 60 starts to rotate following the output shaft 53 while slipping due to the frictional engagement force with the one-way clutch coil spring 61, and the rotational speed gradually increases. And the impeller 60
The lever 62 that rotates integrally with the engaging member 6 is rotated by centrifugal force.
4 is engaged with the engaging portion 64a. Since the engagement member 64 is fixed to the output shaft 53, the impeller 60 and the output shaft 53 are directly connected to each other via the engagement member 64 and the lever 62. As a result, the impeller 60 has the output shaft 53.
It directly receives the rotational force of and rotates without slipping.

[0008]

However, in the structure of this Japanese Patent Application No. 6-329792, in order to reliably operate the lever 62 which constitutes a so-called centrifugal clutch,
It is necessary to take measures to protect the lever 62 from foreign matters and burrs that obstruct the movement of the lever 62. That is, it is necessary to take sufficient dust countermeasures during manufacturing. Further, a step of removing burrs from the lever 62, the engaging member 64, etc., which are components, is required. For this reason, the manufacturing efficiency is deteriorated and the cost is increased. Further, when the impeller 60 is locked by some force, centrifugal force is not generated and the rotor 52 continues to rotate. Therefore, the boss member 59 and the one-way clutch coil spring 61 that constitute a so-called friction clutch are abnormal. It becomes worn and the friction function deteriorates.

Therefore, according to the present invention, when the load is rotated by the synchronous motor, the load is surely rotated in one direction without malfunction, and when the load such as the impeller is locked, the rotation of the rotor is stopped and the friction clutch is abnormal. It is an object of the present invention to provide a drive device for a synchronous motor that prevents abrasion.

[0010]

To achieve the above object, a drive device for a synchronous motor according to a first aspect of the present invention engages a synchronous motor and a rotor of the synchronous motor, and transmits only rotation in a predetermined direction of the rotor. A possible one-way rotation transmission mechanism, a first rotating body that integrally rotates only in a predetermined rotation direction of the rotor by the one-way rotation transmission mechanism, an output shaft for rotating a load, the output shaft and the first play. A second rotating body, which is integrally rotatable and connectable with a space and is also integrally rotatable with a second play space, and a first rotating body and a second rotating body are connected to the rotor. A unidirectional frictional rotation transmission mechanism is provided which transmits frictional rotation only in a predetermined direction and integrally rotates when the rotor rotates in a direction opposite to the predetermined direction.

According to a second aspect of the present invention, there is provided a drive device for a synchronous motor, wherein the synchronous motor and a rotor of the synchronous motor are engaged with each other, frictional rotation transmission is performed only in a predetermined direction rotation of the rotor, and in a direction opposite to the predetermined direction of the rotor. During one rotation, the one-way friction rotation transmission mechanism rotates integrally, the first rotation body frictionally rotates only in a predetermined rotation direction of the rotor by the one-way friction rotation transmission mechanism, the output shaft for rotating the load, and the output. A second rotating body that can be integrally rotationally connected to the rotor with a first clearance between the shafts, and can be integrally rotationally connected to the rotor with a second clearance to the rotor, a first rotating body and a second rotating body. The rotating body and a one-way rotation transmitting mechanism capable of integrally transmitting rotation of the rotor only in a predetermined direction.

Furthermore, the invention of claim 3 is the drive device for a synchronous motor of claim 1, wherein any one of a ratchet mechanism, a roller mechanism, and a lever mechanism is adopted as a one-way rotation transmission mechanism, and one-way friction rotation is performed. As the transmission mechanism, either a coil spring mechanism or a friction plate mechanism is adopted.

According to a fourth aspect of the present invention, in the drive device for a synchronous motor according to the first aspect, the load is an impeller for absorbing and discharging fluid, and the output shaft is a shaft fixed to the impeller and penetrating the rotation center of the rotor. There is.

Therefore, in the drive device for a synchronous motor according to the first aspect, when an alternating current is applied to the synchronous motor, the rotor of the synchronous motor starts left-right rotational vibration due to the alternating magnetic field and rotates in an appropriate direction. start. When the direction is opposite to the predetermined direction, the rotation of the rotor is
The rotor rotates as it is without being transmitted to the rotating body. Then, the rotor moves to the second play interval after passing through the second play interval section.
Connect with the rotating body of. After that, after a section of the first play interval, the rotor also connects with the output shaft and tries to rotate the load. However, since the force required to raise the load to the synchronous rotation is larger than the rotational force of the rotor, the rotor cannot continue rotation and is inverted in the predetermined direction.

When the rotor rotates in a predetermined direction,
The one-way rotation transmission mechanism rotates the first rotating body in a predetermined direction. Then, this rotation is transmitted to the second rotating body via the one-way frictional rotation transmitting mechanism, and causes the second rotating body to rotate with no load in the section of the first play interval. When this play disappears, the rotation of the rotor is the one-way rotation transmission mechanism, the first rotation body, the one-way friction rotation transmission mechanism, the second rotation body,
It is transmitted to the load via the output shaft. But at this time,
The one-way frictional rotation transmission mechanism is not an integral rotation but a frictional rotation, and the second rotating body rotates in a predetermined direction with a delay with respect to the first rotating body while sliding. This sliding torque causes the load to gradually increase in rotation. This state continues until the rotor is connected to the second rotating body after passing through the second play interval section. Then, when the rotor is integrally and rotationally connected to the second rotating body, a load force is applied to the rotor, but since the rotation of the load has sufficiently risen, the rotational force of the rotor is sufficiently larger than the force received from the load. Therefore, the rotor continues to rotate synchronously.

According to a second aspect of the present invention, the one-way friction and rotation transmission mechanism is arranged in the one-way rotation and transmission mechanism according to the first aspect, and similarly, the one-way friction and rotation transmission mechanism is also rotated in one direction. Since the transmission mechanism is arranged, the same operation as the drive device for the synchronous motor according to claim 1 is produced. That is, when the rotor rotates in the direction opposite to the predetermined direction, the rotor cannot continue the rotation and is inverted. When the rotor rotates in a predetermined direction, the load gradually increases due to the slip torque. Then, even after the rotor is integrally rotationally connected to the second rotating body,
The rotor continues to rotate in the predetermined direction.

Further, in the invention of claim 3, in the drive device for a synchronous motor of claim 1, a mechanism such as a ratchet mechanism is adopted as the one-way rotation transmission mechanism, and a coil spring is used as the one-way friction rotation transmission mechanism. Since the mechanism such as the mechanism is adopted, the rotation at the time of rising of the rotor in the predetermined direction is transmitted to the first rotating body through any one of the ratchet mechanism, the roller mechanism and the lever mechanism. . Then, the rotation of the rotor in the predetermined direction is frictionally transmitted from the first rotating body to the second rotating body via either the coil spring mechanism or the friction plate mechanism.

Further, in the invention of claim 4, the impeller as a load is started and rotated only in a predetermined direction, and a fluid such as water is sucked and discharged by the impeller.

[0021]

BEST MODE FOR CARRYING OUT THE INVENTION The structure of the present invention will be described below in detail based on an example of an embodiment of the invention shown in the drawings.

1 to 11 show an example of an embodiment in which the drive device for a synchronous motor of the present invention is applied to a centrifugal pump. The centrifugal pump includes a drive unit 1 including a synchronous motor 3 and the like, and an impeller 4 that is driven by the synchronous motor 3 to rotate.
And a pump section 2 including the above.

The synchronous motor 3 arranged in the drive unit 1 has a rotor 6 composed of a stator core 5 and a permanent magnet rotor, an output shaft 7 rotatable with respect to the rotor 6, and a magnetic path piece 8 of the stator core 5. , The drive coils 9, 9, the magnetic pole portion 10 of the stator core 5,
10, bearings 11, 11 of the output shaft 7, these bearings 11,
It is mainly composed of a resin-made cylindrical case 12 that holds 11. Here, the main configuration of the cylindrical case 12 is composed of a cylindrical portion 12a, a disc portion 12b, and a flat plate portion 12c. The cylindrical portion 12a, the disc portion 12b, and the flat plate portion 12c are integrally formed, and the disc portion 1
A through hole into which the output shaft 7 is rotatably inserted is provided at the center of 2b. The cylindrical portion 12a is press-fitted into the stator core 5 such that the outer surface of the cylindrical portion 12a contacts the inner surfaces of the magnetic pole portions 10 of the fixed iron core 5. The portion of the disc portion 12b facing the pump portion 2 forms part of the pump portion 2.

At one end of the rotor 6, the rotor 6
Is provided with a rotor disk 6a integral with the center boss, and the rotor disk 6a is provided with a concave portion 6b having a saw-toothed wall 6d and a radial hitting convex portion 6c.

A claw body 13 as a first rotating body having engaging holes 13a, 13a and claw portions 13b, 13b is placed in the recess 6b of the rotor board 6a. The sawtooth-shaped wall 6d and the pawl portion 13b constitute a ratchet mechanism that is a one-way rotation transmission mechanism. The projections 14a and 14a of the collar body 14 are inserted into the engaging holes 13a and 13a of the pawl body 13 to position the pawl body 13. Further, a torsion coil spring 15 as a friction means is wound around the outer peripheral surface of the collar body 14 so as to tighten the collar body 14. The inner diameter of the torsion coil spring 15 is designed to be smaller than the outer diameter of the collar body 14, and the torsion coil spring 15 is wound around the outer periphery of the collar body 14 while being expanded in diameter.

On the other side surface of the collar body 14, a clutch plate 16 as a substantially disk-shaped clutch body is arranged in contact with the collar body 14. An engaging groove 16a extending in the circumferential direction is formed on one end surface of the clutch plate 16, and one end 15a of the torsion coil spring 15 is inserted into the engaging groove 16a to restrict movement in the circumferential direction. . The engagement groove 16a, the torsion coil spring 15, and the collar body 14 form a one-way friction rotation mechanism. In addition, on the outer peripheral portion of the clutch plate 16, the projections 1 that are axially extended are provided.
6b is provided, and the hitting projection 16b is configured so that the hitting projection 6c of the rotor 6 abuts with a certain play interval. The play interval is defined as the first play interval. The other end surface of the clutch plate 16 in the axial direction is provided with a pin accommodating recess 16c for accommodating the pin 7a fixed to the output shaft 7 and pin-degree contact projections 16d, 16d with which the pin 7a abuts. Then, the pin 7a is pressed against the b convex portions 16d and 16d per pin degree.
Are configured to abut with a certain play interval. It should be noted that this play interval is defined as the second play interval.

On the other hand, a leaf spring 17 is arranged at the end of the rotor 6 opposite to the rotor disk 6a. This leaf spring 1
7 is pressed by the pressing plate 18, and as a result, presses the rotor 6. This holding plate 18
The sliding is restricted by a stop pin 7b or an E-shaped stop ring that is fixed substantially orthogonal to the output shaft 7. By the action of the leaf spring 17 and the like, the rotor 6 is prevented from sliding in the axial direction, and the uneven rotation of the rotor 6 is suppressed.

Next, the detailed structure of the synchronous motor 3 and its periphery will be described.

As shown in FIG. 3, the stator core 5 of the synchronous motor 3 has a structure in which a laminated iron core is integrated by a pin 19. Further, the faston terminals 21, 21, 2 are provided on the hook portion of the bobbin 20 around which the drive coils 9, 9 are wound.
Terminal portions 22, 22, 22 into which 6 is fitted are provided. Further, a thermal fuse 23 is arranged around the drive coils 9 and 9 to prevent the temperature of the synchronous motor 3 from rising too much due to overload or the like.

The bearing 11 on the side opposite to the pump portion 2 is
It is press-fitted into the recess of the bearing holder 23 via an oil impregnated felt 24. On the other hand, the bearing 11 on the pump unit 2 side
Is a fitting recess 12d provided at the center of the disc portion 12b.
Is press-fitted via the oil impregnated felt 25.

In the parts of the drive unit 1, the output shaft 7
The only parts that are fixed to are the pin 7a and the stop pin 7b. That is, the other parts of the drive unit 1 shown in FIGS. 4 and 5 are not fixed to the output shaft 7, but are inserted so that the output shaft 7 is rotatable. The drive unit 1 including the synchronous motor 3 is covered with the drive unit case body 27. The drive unit case body 27 has a plurality of heat dissipation holes 27a, engagement holes 27b with which power source connection terminals (not shown) for connecting to the faston terminals 21 are engaged, and the flat plate portion of the cylindrical case 12. An engaging portion 27c with which the fitting portion 12j formed in 12c is engaged is provided.

Next, the structure of the pump section 2 will be described in detail.

An oil seal 30 is provided in the second fitting recess 12i in the substantially central portion of the disc portion 12b of the cylindrical case 12 to ensure airtightness between the disc portion 12b and the cylindrical portion 12a. The output shaft 7 penetrates the oil seal 30, and the impeller 4 is fixed to the tip of the output shaft 7.

Then, the pump case 31 is fitted and fixed to the disc portion 12b so as to cover the impeller 4 and the like. The pump case 31 is provided with an inlet portion 31a for sucking water and an outlet portion 31b for discharging water, and the outlet portion 31b is formed in a substantially radial direction from the center of rotation of the impeller 4. ing.

Here, in order to prevent the inflowing water from leaking out of the cylindrical case 12 and the pump case 31, the O-ring 32 having elasticity in the circumferential groove 12e of the disk portion 12b.
The flange portion 31c of the pump case 31 is attached to the stopper portion 12f of the edge portion of the disc portion 12b by the O-ring 32.
･ ･ ･ It is pressed down to 12f. The cylindrical case 12 and the pump case 31 are fitted to each other by inserting the protrusion 31d of the flange portion 31c of the pump case 31 into the notches 12g, ..., 12g of the disc portion 12b, and then the protrusion 31d Cylindrical case 1 until the side surface comes into contact with the rotation contact portion 12h, ..., 12h of the disk portion 12b.
2 and the pump case 31 are rotated with respect to each other. The flat plate portion 12c has a plurality of heat dissipation holes 12k.
Is provided.

The impeller 4 is fixedly attached by locking the inner protrusion 4a of the impeller 4 by a bush 32 that is press-fitted or inserted into the tip of the output shaft 7.
This is because when the centrifugal pump is operated, the upward force F shown in FIG. 1 is applied to the impeller 4 and the impeller 4 is easily removed from the output shaft 7. In this example, the cap 33 is screw-engaged with the tip of the output shaft 7 in order to completely prevent the retainer from coming off. In order to position the impeller 4, a step portion 7c is formed on the output shaft 7, and the step portion 7c and the bush 32 sandwich the inward protruding portion 4a.

The centrifugal pump thus constructed is assembled as follows.

First, when assembling the peripheral portion of the rotor 6 of the synchronous motor 3, the clutch plate 16 is rotatably fitted to the output shaft 7 having the pin 7a implanted therein. And this clutch plate 1
The collar body 14 in which the torsion coil spring 15 is wound around the central concave portion of 6 is fitted so that one end 15a of the coil spring 15 enters the engaging groove 16a of the clutch plate 16. Then, the pawl body 13 is engaged with the collar body 14. Next, the rotor 6 is rotatably fitted to the output shaft 7, and the pawl 13 is fitted into the recess 6b of the roller board 6a. Then, the leaf spring 17 and the pressing plate 18 press the rotor 6,
In this state, the stop pin 7b is fixed to the output shaft 7. Also,
The bearings 11, 11 are fitted to both sides of the rotor 6, and the assembled rotor 6 and the like are inserted from the open end of the cylindrical portion 12 a of the cylindrical case 12. At this time, the output shaft 7 is the disc portion 1
The clutch plate 1 is rotatably inserted into the through hole at the center of 2b.
The bearing 11 adjacent to 6 is supported by the bearing holder 23 via the felt 24. Then, the bearing holder 23 is fitted into the opening end of the cylindrical portion 12a.

After that, the oil seal 30 is engaged so that the output shaft 7 is inserted through the center thereof, and the disk portion 12 is inserted.
It is arranged so as to fit into the second fitting recess 12i of b. Then, the impeller 4 is locked to the output shaft 7 so that the inward projection 4 a thereof engages with the step 7 c of the output shaft 7. Then, the bush 32 is press-fitted or inserted, and the inward projection 4a is sandwiched between the bush 32 and the step 7c. Then, the cap 33 is screw-engaged with the output shaft 7. Finally, the cylindrical portion 12a is press-fitted into the fixed iron core 5 having the drive coils 9 and 9 and the bobbin 20 to engage and fix the drive case body 27 in the cylindrical case 12, and the pump case 31 in the cylindrical case. Fit and fix to 12.

Next, the operation of the drive device for the synchronous motor configured as described above will be described.

When an AC voltage is applied to the drive coils 9, 9 of the synchronous motor 3, the rotor 6 begins to oscillate left and right due to the alternating magnetic field and is rotated in either direction. When the direction rotates in the direction opposite to the predetermined direction, that is, the direction indicated by the arrow A in FIG. The rotation is not transmitted to the pawl body 13, which is the first rotary body. Therefore, the rotor 6 idles, the contact projection 6c of the rotor 6 shifts from the state of FIG. 11A to the state of FIG. 11B, and the contact projection of the clutch plate 16 that is the second rotating body is rotated. 16b. The section up to this time is called the second play interval. After that, the clutch plate 16
As the rotor 6 rotates together, the pin 7a of the output shaft 7 comes into contact with the pin projections 16d and 16d, resulting in the state shown in FIG. 11C. 1st section until hitting the pin 7a
It is called the play interval.

When the section of the first and second play intervals disappears, that is, when the state of FIG. 11C is reached,
The rotor 6 is loaded with the impeller 4 and water. However, since it takes a very short time for the rotor 6 to change from the state shown in FIG. 11A to the state shown in FIG.
Is not large, and the total load by the impeller 4 and water acts as a very large load because they are in a stopped state. For this reason, the rotational force of the rotor 6 is lost by the total load of the impeller 4 and water, and the rotor 6 cannot rotate continuously and reverses. That is, the rotation starts in the direction of arrow B in FIG.

When the rotor 6 rotates in the direction of the arrow B, first, the sawtooth-shaped wall portion 6d causes the pawl portions 13b, 1 of the pawl body 13 to rotate.
Engage 3b. That is, the clutch is engaged. Therefore, the pawl body 13, which is the first rotary body, rotates in the B direction, and the collar body 14 engaged with the pawl body 13 also rotates in the B direction. Then, the clutch plate 16 engaged with the collar body 14 via the torsion coil spring 15
Rotates in the B direction and hits the pin 7A with a pin 16
d and 16d are hit. That is, the state shown in FIG. The rotor 6 is shown in FIG.
Rotate with no load until the state of (D) is reached.

In the state shown in FIG. 11D, the rotor 6,
The rotation of the rotor 6 is transmitted to the impeller 4 through the path of the pawl body 13, the collar body 14, the torsion coil spring 15, the clutch plate 16, the pin 7a, and the output shaft 7. Here, the total load due to the impeller 4 and water is large, but at this time, the torsion coil spring 15 is twisted on the loose side, and the collar body 14 rotates integrally with the rotor 6 while sliding with respect to the torsion coil spring 15. On the other hand, the collar body 14 and the torsion coil spring 1
A slip torque due to this slip acts between the impeller 4 and 5, and part of the rotational force of the rotor 4 is transmitted to the impeller 4, and the impeller 4 gradually starts to rotate. That is, FIG. 11 (E)
, The pin 7a starts rotating in the B direction. And
The rotor 6 continues to rotate, and the bumps 6c
Hit the projection 16b of the clutch plate 16,
The state shown in FIG. 11 (F) is obtained.

In the state of FIG. 11F, the rotation of the rotor 6 is directly transmitted to the output shaft 7 via the clutch plate 16, so that the total load of the impeller 4 and water is directly applied to the rotor 6. However, the impeller 4, that is, the output shaft 7 is starting to rotate, and the rotational force of the rotor 6 is larger than the total load of the impeller 4 and water. For this reason,
The rotor 6 can continue to rotate while maintaining the positional relationship of FIG.

In this way, the magnitude of the load applied to the rotor 6 differs depending on the rotation direction of the rotor 6, so that the rotor 6 is always started and rotated in the rotation direction in which the load is light, that is, in the B direction in the examples of FIGS.

When the impeller 4 is rotated in synchronization with the rotor 6, water is sucked from the inlet 31a of the pump case 31 and discharged from the outlet 31b. At this time, the outlet portion 31b has a shape that is oriented in the radial direction from the central portion of the pump case 31, so that when the impeller 4 rotates, the force of the arrow F shown in FIG. The impeller 4 causes the output shaft 7
Never leave. In addition, the output shaft 7 is prevented from moving largely upward in FIG. 1 by the stop pin 7b.

By the way, it is assumed that the state of FIG. 11 (F) is reached when the voltage application is terminated and the rotation of the impeller 4 and the rotor 6 is stopped. At this time, if the voltage is reapplied, the rotor 6 to the impeller 4 are integrally rotated even if an attempt is made to rotate in the B direction, which is the same direction as that immediately before, so that the load is Does not start up. Therefore, it is once rotated in a direction opposite to the immediately preceding rotation direction, that is, in the A direction. However, in the opposite direction, as described above, the rotational force of the rotor 6 becomes smaller than the load of the impeller 4 and the like, and the rotation cannot be continued. And
The rotation in the B direction will continue based on the principle described above.

Therefore, according to this embodiment, the rotor 6 always reliably rotates in one direction. Further, if the impeller 4 is blocked from rotating for some reason and enters a locked state, the rotation of the rotor 6 also stops, so that the torsion coil spring 15 serving as a friction clutch and the collar body 14 are abnormally worn. Does not happen.

Further, in this embodiment, the contact projection 6c of the rotor 6 is replaced by the projection 16b of the clutch plate 16.
And the pin 16b, 16d, 16
The rotation of the rotor 6 is transmitted to the impeller 4 with a structure in which d contacts the pin 7a. For this reason, even if the rotation unevenness of the rotor 6 or the variation of the load of the impeller 4 occurs during the synchronous rotation of the rotor 6 and the impeller 4, the slips acting between the rotor 6 and the impeller 4 cause the uneven rotation and the load. Buffer fluctuations. Therefore, the rotation of the impeller 4 can be stabilized. Furthermore, according to this embodiment, the one-way rotation transmission mechanism is a structure that operates only in the friction transmission section, and thus the one-way rotation transmission mechanism is not overloaded,
Long life. That is, when the load that causes the impeller 4 to rotate synchronously with the rotor 6 becomes large, the protrusion 6c of the rotor 6 which is a high strength portion, the protrusion 16b of the clutch plate 16 and the protrusion 16d of the pin contact 16d. , 16d
And the pin 7a are integrally connected, and the rotation of the rotor 6 is transmitted.

In addition, since the pawl body 13 is sandwiched and held between the collar body 14 and the rotor 6, the pawl portion 13
b, 13b can be prevented from being deformed in the axial direction, and the pawl portion 13b,
The transmission force by 13b can be improved.

In a device that drives a load member placed in a highly viscous fluid, such as this centrifugal pump, which is an example of the embodiment, the moving acceleration of the fluid can be reduced at the initial stage of rotation of the rotor 6, With the small output synchronous motor 3, the load members such as the impeller 4 can be rotationally activated, and
It is possible to gradually increase the fluid acceleration and increase the discharge amount. Therefore, not only the device can be downsized, but also sudden discharge of the fluid can be prevented. Moreover, when the rotor 6, the clutch plate 16, and the output shaft 7 are rotated in unison, the discharge amount by the impeller 4 becomes extremely stable.

Further, since the frictional force between the collar body 14 and the clutch plate 16 changes as the tightening force of the torsion coil spring 15 changes, the frictional force appropriate for the starting force of the rotor 6 and the magnitude of the external load is changed. You can get the power. That is, if the starting force of the rotor 6 is large and the external load is large,
Since the torsion coil spring 15 is greatly expanded in diameter, the frictional force becomes small. On the other hand, if the starting force of the rotor 6 is small and the external load is small, the torsion coil spring 15 is expanded only slightly and the frictional force becomes large. Further, even when the outside of the collar body 14 is worn due to long-term use, friction always occurs as long as the outer diameter of the collar body 14 is larger than the inner diameter of the torsion coil spring 15. Therefore, the frequency of replacement of the collar body 14 can be reduced.

The above-described embodiment is an example of a preferred embodiment of the present invention, but the present invention is not limited to this, and various modifications can be made without departing from the gist of the present invention. . For example, as the one-way rotation transmission mechanism, a roller mechanism shown in FIG. 12 (A) or a lever mechanism shown in FIG. 12 (B) can be adopted in addition to the ratchet mechanism. That is, as shown in FIG. 12A, the roller 41 is interposed between the first rotating body 40 and the rotor 6.
Further, as shown in FIG. 12B, the lever 43 is provided on the first rotating body 42, and the lever 4 is centered around the rotation fulcrum 44.
It is possible to provide a spring (not shown) that applies a moving force (arrow G) in the outer diameter direction of 3 to form a one-way rotation mechanism.

Further, in the example of the embodiment shown in FIGS. 1 to 11, the torsion coil spring 1 is used as the one-way friction transmission mechanism.
Although the structure using No. 5 is used, any structure that generates friction between the collar body 14 and the clutch plate 16 may be used.
For example, a structure in which the contact surface between the collar body 14 and the clutch plate 16 is roughened, or a friction plate mechanism that holds a friction plate between these members may be used. According to these structures, since the torsion coil spring 15 is not necessary, the thickness of the collar body 14 can be reduced, and the size and weight of the device can be reduced.

Further, in each of the embodiments, the pawl body 13, the clutch plate 16 and the collar, which serve as a one-way rotation transmission mechanism and a one-way friction rotation transmission mechanism, are provided at a position where the rotation of the rotor is transmitted to the output shaft 7. Although a mechanism such as the body 14 is provided, each rotation transmission mechanism may have a structure provided at another position as long as it is provided between the rotor 6 and the load. For example, the rotor 6 and the output shaft 7 may be fixed, and a mechanism such as a clutch plate 16 may be provided at a position where the rotation of the output shaft 7 is transmitted to the impeller 4. Further, the rotor 6 is not inserted into the output shaft 7, but the rotation of the rotor 6 is caused to rotate the output shaft 7 via a gear, and the gear transmission portion has a one-way rotation transmission mechanism or a one-way friction rotation transmission mechanism. May be provided. Therefore, a mechanism having an appropriate form can be selected and provided according to the shape of the external load and the like.

Further, in the embodiment shown in FIGS. 1 to 11, the one-way rotation transmission mechanism is provided between the rotor 6 and the pawl body 13 which is the first rotating body. The structure has a one-way friction and rotation transmission mechanism.
Instead of providing the one-way frictional rotation transmission mechanism using the torsion coil spring 15 or the like between the rotating body 13 and the second rotating body 16, the one-way rotation transmitting mechanism may be provided in this portion.

According to the structure shown in each of the embodiments, a large rotation angle can be obtained until the rotor 6 starts rotating and rotates integrally with the output shaft 7. Therefore, slippage until synchronous rotation is performed. The amount increases. Therefore, even if a heavy load is applied, it can be started smoothly,
The starting power is not increased.

The drive device for the synchronous motor of the present invention is
Although it is suitable for a device with a high load such as a centrifugal pump, it can be generally applied to a device that drives a load member using a synchronous motor as a drive source.

[0059]

As is apparent from the above description, in the drive device for a synchronous motor according to the first and second aspects, the rotor can be reliably rotated in one direction, and stable starting rotation can be obtained. Moreover, when the load of the impeller or the like is locked, the rotation of the rotor also stops, so the one-way frictional rotation transmission mechanism does not wear abnormally, and the life of the device can be extended. Moreover, since the one-way rotation transmission mechanism works only in a short time until the rotor and the output shaft rotate integrally and when the load does not increase, the one-way rotation transmission mechanism and the drive device incorporating this mechanism. Has a long life. In addition, it is possible to obtain a sufficient rotation angle until the rotor starts to rotate synchronously with the external load, and even if the external load is large, the starting power does not increase and small power consumption is achieved. Can be realized.

Further, according to the invention of claim 3,
As one-way rotation transmission mechanism and one-way friction rotation transmission mechanism,
Since a mechanism with a simple structure such as a ratchet mechanism is adopted,
The entire mechanism does not become complicated and is suitable for downsizing.
In addition, according to the invention described in claim 4, the rotation of the impeller can always be reliably activated in a fixed direction, and the fluid can be stably supplied and discharged.

[Brief description of drawings]

FIG. 1 is a schematic cross-sectional view of an example of an embodiment of the present invention.

FIG. 2 is a partially omitted exploded perspective view showing an example of an embodiment of the present invention.

FIG. 3 is an exploded perspective view showing a fixed portion of the synchronous motor.

FIG. 4 is an exploded perspective view showing a one-way rotation transmission mechanism, a one-way friction rotation mechanism, and a peripheral portion thereof.

FIG. 5 is an exploded perspective view showing a cylindrical case and its peripheral portion.

FIG. 6 is a view showing a color body, (A) is a side view thereof,
(B) is the top view.

FIG. 7 is a view showing a state in which a torsion coil spring is wound around a collar body, (A) is a side view thereof, and (B) is a plan view thereof.

FIG. 8 is a view showing a clutch plate, (A) is a plan view thereof,
(B) is a side view thereof, and (C) is a bottom view thereof.

FIG. 9 is a view showing a state where a pawl body is fitted to a rotor board.

FIG. 10 is a schematic cross-sectional view showing a rotor and its peripheral portion.

FIG. 11 is a diagram for explaining the operation of the present invention, and is a diagram showing each positional relationship among the rotor, the output shaft, and the second rotating body at each operation time point.

FIG. 12 is another example of the one-way rotation transmission mechanism used in the present invention, in which (A) shows a roller mechanism and (B) shows a lever mechanism.

FIG. 13 is a cross-sectional view showing a drive device for a synchronous motor, which the applicant of the present invention has previously filed.

14 is a sectional view taken along line XIV-XIV in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Drive part 2 Pump part 3 Synchronous electric motor 4 Impeller (load) 6 Rotor 6d Serrated wall (one-way rotation transmission mechanism) 7 Output shaft 7a pin 13 Claw body (1st rotating body) 13b Claw part (one-way rotation) Transmission mechanism) 14 Color body (one-way friction rotation transmission mechanism) 15 Torsion coil spring (one-way friction rotation transmission mechanism) 16 Clutch plate (second rotation body) 16a Engagement groove (one-way friction rotation transmission mechanism)

Claims (4)

[Claims] 1. A synchronous motor, a one-way rotation transmitting mechanism that engages with a rotor of the synchronous motor, and is capable of transmitting rotation only in a predetermined direction rotation of the rotor, and a predetermined rotation direction of the rotor by the one-way rotation transmitting mechanism. Only a first rotating body that rotates integrally, an output shaft for rotating a load, and a first play interval with this output shaft that can be integrally and rotatably connected, and a second play interval with the rotor. The second rotating body, which is integrally rotatable and connected, and the first rotating body and the second rotating body frictionally transmit only the rotation of the rotor in a predetermined direction and is opposite to the predetermined direction of the rotor. A driving device for a synchronous motor, comprising a one-way frictional rotation transmission mechanism that integrally rotates when rotating in one direction. 2. A one-way frictional rotation engaged with a synchronous motor and a rotor of the synchronous motor, transmitting frictional rotation only in a predetermined direction rotation of the rotor, and integrally rotating when the rotor rotates in a direction opposite to the predetermined direction. A transmission mechanism, a first rotating body that frictionally rotates only in a predetermined rotation direction of the rotor by the one-way friction rotation transmission mechanism, an output shaft for rotating a load, and a first play gap of the output shaft are provided. And a second rotating body that is integrally rotatable and connectable with the rotor and has a second clearance between the rotor and the first rotating body.
Drive device for a synchronous motor, comprising: a unidirectional rotation transmission mechanism capable of integrally transmitting rotation of the rotor and the second rotor only in a predetermined direction of rotation of the rotor. 3. A ratchet mechanism, a roller mechanism, or a lever mechanism is adopted as the one-way rotation transmission mechanism, and a coil spring mechanism or a friction plate mechanism is adopted as the one-way friction rotation transmission mechanism. The drive device for a synchronous motor according to claim 1, wherein: 4. The synchronous motor according to claim 1, wherein the load is an impeller for absorbing and discharging a fluid, and the output shaft is a shaft fixed to the impeller and penetrating a rotation center of the rotor. Drive.