JPS6359829A - Spinning reel - Google Patents

Abstract

(57) [Abstract] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a fishing reel, and particularly to a spinning reel.

[Conventional technology]

In conventional spinning reels, the power transmission path from the handle to the rotor is fixed to one path.
Therefore, the gear ratio there was also fixed to one gear.

(Problem to be solved by the invention) In a fishing reel, when no fish is hooked,
It is preferable that the gear ratio be large in order to quickly wind up the line, but when a fish is hooked, it is preferable that the gear ratio be small in order to apply a large force (q). However,
In conventional spinning reels, as mentioned above, the gear ratio was always fixed at one value, so
Because the angler must compromise and set the actual gear ratio to a value midway between the desired gear ratio when no fish are caught and the desired gear ratio when fish are caught, anglers In both cases, there is a problem in that the reel must be operated with a gear ratio that is not optimal.

(Purpose of the Invention) The present invention was made to solve the above-mentioned problems of the conventional technology. The purpose of the present invention is to provide a spinning reel with a machine groove.

(Means for Solving the Problems) FIG. 9 is a block diagram conceptually showing the present invention, and as shown in this figure, the spinning reels according to the present invention are each rotatably supported by a reel body. a handle shaft 2 and a rotor 24, each with an output end connected to the rotor 2.
The first power transmission path 101 and the second power transmission path 102 connected to torque limiter means 103, the handle l1jli12 and the second power transmission path 1.
02, and a one-sided clutch means 104 that transmits torque in only one direction G7,
When the handle shaft 2 is rotating in the normal direction and the input and output sides of the torque limiter means 104 are rotating together, the rotational speed of the input end of the second power transmission path 102 is higher than that of the input end of the second power transmission path 102. The rotational speed is set to be faster than the input side rotation speed of the one-way clutch means 104, and the torque limiter means 103c is rotated from the handle shaft 2 to the input side of the one-way clutch means 104.
The speed ratio of the high-speed power transmission path (rotation speed of the rotor/rotation speed of the handle shaft) from the handle shaft 2 to the rotor 24 via the first power transmission path 101 is This is higher than the speed ratio of the low-speed power transmission path that reaches the rotor 24 via the directional clutch means 104 and the second power transmission path 102.

[Effect]

In the present invention, when no fish is hooked, the acting torque is small, so the input side and the output side of the torque limiter means 103 rotate integrally, and the power is transmitted from the handle IIIIII2 to high-speed power transmission. path, namely the torque limiter means 103 and the first power transmission path 10
1 to the rotor 24. Since this high-speed power transmission path has a large speed ratio, the rotor 24 is rotated at high speed and the yarn is wound at high speed. Incidentally, at this time, the output side of the one-way clutch means 104, that is, the input end of the second power transmission path 102 is connected to the clutch means 10.
4, the one-way clutch means 104 is not transmitting torque.

On the other hand, when a fish is caught and a torque of more than a predetermined value is applied, the torque limiter means 103 enters a slip state, and the one-way clutch means becomes connected to transmit torque. Therefore, the power is mainly transmitted from the handle shaft 2 to the low-speed power transmission path, that is, the one-way clutch means 1.
04 and the second power transmission path 102 to the rotor 24. Since this low speed power transmission path has a small speed ratio, it is possible to obtain a large force.

(Example) Hereinafter, the present invention will be explained based on embodiments shown in the drawings.

1 to 6 show an embodiment of a spinning reel according to the present invention. In this embodiment, boss portions 1a are provided at opposing positions on both sides of the reel body 1, respectively.
, 1b are provided, and a handle shaft 2 is inserted through these boss portions 1a, 1b in a manner rotatable relative to the main body 1.

A male threaded portion 3a which is screwed onto the end of the handle 3 is screwed into the −ψi; portion of the handle 4III]2, thereby connecting the handle 3 to the handle shaft 2.

Near the ends of the handles 111 and 112 on the boss 1a side, the parts forming 180 degrees to each other are cut flat and parallel to each other, thereby forming two flat parts 2a and having a non-circular cross section. There is.

A ball bearing 4 is interposed between the flat portion 2a installation portion of the handle shaft 2 and the boss portion 1a. In addition, the handle shaft 2 has a boss 1b on the flat part 2a installation part.
A collar portion 2b is provided in contact with the side end portion. A pawl mold 5 and a washer 6 are interposed between the collar portion 2b and the ball bearing 4 so as to be passed through the handle shaft 2.

As shown in FIG. 2, the claw mold 5 has, at its center,
A non-circular hole 5a corresponding to the cross-sectional shape of the flat part 2a of the handle shaft 2 is provided, and the neck part of the flat part 2a of the handle shaft 2 is fitted into this hole 5a. It cannot rotate about axis 2.

Similarly, in the vicinity of the end of the handle shaft 2 on the boss portion 1b side, two flat portions 2 are formed by cutting the portions that are 180 degrees apart flat and parallel to each other.
C and has a non-circular cross section. A main gear 7 is fitted in a portion of the handle shaft 2 between the plane part 2C installation part and the flange part 2b so as to be rotatable with respect to the handle shaft 2. Face gear 7a
and a spur gear 7b integrally.

On the side surface of the face gear 7a of the main gear 7, as shown in FIGS.
They are each rotatably supported by a shaft 41 at the 0 degree position. These claws 40 are connected to springs 4.
2, it is urged toward the claw mold 5. Here, the pawl type 5, pawl 40, etc. constitute a one-way clutch means in this embodiment, and when the handle shaft 2 is rotated in the forward rotation direction (in the direction of the arrow), the main gear 7 is rotated. If the main gear 7 is not rotated in the same direction at a faster rotational speed than the handle shaft 2, the pawl type 5 and the pawl 40 will mesh, but when the main gear 7 is rotated in the same direction at a faster rotational speed than the handle 'F[l12]. The claw mold 5 and the claw 40 are arranged so as not to mesh with each other.

In the flat part 2C installation part of the handle shaft 2, in order from the post 1a side to the post 1b side, there are a shaft side member 8, a friction plate 9, a high speed gear 10, a friction plate 11, a shaft side member 12, and a friction plate 13. ,
High speed gear 14, friction plate 15, shaft side member 16, ball bearing 1
7 and the annular spring receiver are mounted with plates 18 adjacent to each other.

The shaft side member 12 is made of metal and has a disk shape, and as shown in FIG.
A non-circular hole 12a corresponding to the cross-sectional shape of the CKQ holder is provided, and the handle 'Ti
Since it is fitted into the neck portion of the flat portion 2C of 112, it can move in the axial direction with respect to the handle shaft 2, but cannot rotate.

The other shaft-side members 8 and 16 have the same configuration as the shaft-side member 12, and can move in the axial direction with respect to the handle fIII2, but cannot rotate (however,
Since the shaft-side member 8 is in contact with the end of the flat portion 2C of the handle shaft 2 on the post 1a side, it cannot move any further toward the post 1a).

The high-speed gear 10 has a circular hole 10a in the center as shown in FIG. It is movable in the direction and rotatable. Furthermore, with a similar configuration, another high-speed gear 14 is also movable and rotatable in the axial direction with respect to the handle shaft 2.

The friction plate 9.11.13.15 is made of asbestos or other material with a large coefficient of friction, has an annular shape, and is axially oriented with respect to the handle shaft 2 like the high-speed gear 10.14. It is said to be movable and rotatable.

The ball bearing 17 is connected to the handle shaft 2 and the boss portion 1b of the main body 1.
It is loosely fitted between the inner surface of the That is, the ball bearing 17 has an inner circumferential surface of its inner ring fitted to the handle shaft 2 so as to be movable in the axial direction, and an outer circumferential surface of its outer ring fitted to the inner circumferential surface of the boss portion 1b of the main body 1 in the axial direction. are movably fitted. The shaft side member 16 has an outer diameter that contacts only the inner ring of the ball bearing 17, while the plate 18 of the spring receiver has an outer diameter and an inner diameter that contact only the outer ring of the ball bearing 17.

Reference numeral 19 denotes an adjustment member having a roughly stepped cylindrical shape, and the small diameter portion 1
9a, and a large diameter portion 19b provided at one end of the small diameter portion 19a.

A male screw 19G is provided on the outer peripheral surface of the small diameter portion 19a, and this male screw 190 is screwed into a female screw 1C provided on the inner peripheral surface of the outer end side of the boss portion 1b of the main body 1. There is. Roughly speaking, a stepped portion 19d is provided on the inner circumferential side of the adjustment member 19, and a compression coil spring 20 is interposed between this stepped portion 19d and the spring support plate 18. A spring receiver 20 biases the plate 18 toward the post 1a of the main body 1. Further, on the outer circumferential portion of the large diameter portion 19b of the adjustment member 19, an appropriate number of teeth 1 are provided as well shown in FIG.
9e is provided.

Reference numeral 21 denotes an adjustment knob, which has a roughly cylindrical shape with a bottom, and has a round hole 21a in the center of the bottom.
The end of the handle 3 is passed through the round hole 21a.

The inner bottom part of the adjustment knob 21 is provided with four parts 21b for accommodating the large diameter part 19b of the adjustment member 19,
A tooth-like recess 21G is provided on the outer periphery of the recess 21b, as clearly shown in FIG. As a result, the adjustment member 19 and the adjustment knob 21 cannot rotate relative to each other.

A groove 2 extending in the axial direction is formed on the inner surface of the adjustment knob 21.
1d are provided in an appropriate number at equal intervals.

One end of an elongated plate spring 22 is attached to the vicinity of the boss portion 1b of the main body 1, and the other end of this temporary spring 22 is a free end and is integrally provided with a convex portion 22a. ing. This convex portion 22a is the adjustment knob 21.
It is adapted to engage and disengage from the groove 21d.

Here, the shaft side members 8, 12, 16, high speed gears 10, 14, friction plates 9, 11, 13° 15, springs 20
．． The adjustment member 19, adjustment knob 21, etc. constitute a torque limiter means in this embodiment.

A hollow rotor shaft 23 is rotatably supported by the main body 1, and this rotor [N123 extends in a direction perpendicular to the handle shaft 2. A pinion 23a is integrally formed on the outer peripheral portion of the rear end of the rotor shaft 23, and the pinion 23a is meshed with the face gear 7a of the main gear 7. Further, a rotor 24 is fixed to the front end side of the rotor shaft 23, and a bail arm (not shown) is rotatably supported by the rotor 24.

A spool shaft 25 is passed through the rotor shaft 23, and this spool shaft 25 is connected to the main body 1 and the rotor shaft 23.
It is rotatable and movable in the axial direction relative to both. Also, the spool! A spool 26 is fixed to the front end side of the 11ilI25. Said spool 2
6 is a spool shaft 2 by a conventionally known drag device 27.
It is designed to be braked via 5.

A two-stage gear 28 integrally having a small gear 28a and a large gear 28b is rotatably supported on the main body 1,
The small gear 28a is meshed with the high speed gears 10 and 14 at the same time, and the large gear 28b is meshed with the spur gear 7b of the main gear 7.
are interlocked with.

Here, the two-stage gear 28, the main gear 7 and the pinion 2
3a constitutes a first power transmission path provided in this embodiment, while main gear 7 and pinion 23a constitute a second power transmission path. And high speed gears 10, 14.
The gear ratio or speed ratio (rotational speed of main gear 7/rotational speed of high-speed gear 10.14) of the gear train consisting of the two-stage gear 28 and the spur gear 7a of the main gear 7 is a (a>1). There is. Furthermore, the gear ratio or speed ratio (pinion 23
Rotational speed of a/rotational speed of main gear 7) is set to be b (b>1).

An eccentric pin 29 is provided on the side surface of the large gear 28b so as to be eccentric from the axis of the gear 28b.

A crank guide 30 is supported on the spool shaft 25 so as to be immovable in the axial direction and non-rotatable with respect to the spool shaft 25. A straight groove 30 extending in a direction perpendicular to the surface of the drawing (a direction perpendicular to the plane of the drawing)
A is provided. A pot center pin 29 is fitted into this groove 30a. Here, the eccentric pin 29 and the crank guide 30 constitute a crank mechanism that converts the rotational motion of the two-stage gear 28 into linear reciprocating motion of the spool shaft 25 and, by extension, the spool 26.

Next, the operation of this embodiment will be explained with reference to the block diagram shown in FIG. 6 showing the power transmission path of this embodiment.

As the spring 20 presses the spring bearing plate 18, the shaft side members 8, 12, 16, the friction plates 11, 13, 15, and the high speed gears 10, 14 are pressed against each other. Therefore, assuming that the force of the spring 20 is set to an appropriate magnitude, the shaft-side member, friction plate, and high-speed gear will not act between them until a torque of a certain thickness is applied. (By the way, a ball bearing 17 is interposed between the shaft side member 16 and the spring bearing plate 18, and the shaft side member 16 is attached to the inner ring of the ball bearing 17.) Since the plate 18 of the spring bearing is in contact only with the outer ring of the ball bearing 17, even if the shaft side member 16 is rotated together with the handle shaft 2, the plate 18 of the spring bearing and, by extension, the spring 20 will not rotate together. )

Therefore, when no fish is caught and there is no large load on the rotor from photometry, when the handle shaft 2 is rotated in the forward direction by the handle 3, the high speed gear 10.1
4 are shaft side members 8, 12, 16 and friction plates 11, 13.
15 and rotates integrally with the handle shaft 2. Therefore, from the handle shaft 2 to the high speed power transmission path, that is,
Shaft side members 8.12, 16, friction plates 11, 13.15, high speed gears 10, 14. Small gears 28a, 2 of second gear 28
Power is transmitted to the rotor 24 through the path of the large gear 28b of the stepped gear 28, the spur gear 7b of the main gear 7, the face gear 7a of the main gear 7, the pinion 23a, and the rotor shaft 23, and the rotor 24 is rotated. In this embodiment, two high-speed gears 10.14 are provided in order to ensure power transmission from the high-speed gear 10.14 to the two-stage gear 28. Since the gears 10 and 14 perform exactly the same function, it is also possible to combine them into one gear.

Now, the gear ratio or speed ratio of the gear train consisting of the high-speed gears 10, 14, the second gear 28, and the main gear 7 is a (a>1
> Therefore, when power is transmitted through the high-speed power transmission path as described above, the rotation speed of the main gear 7 is faster than the rotation speed of the handle shaft 2, so the electric train 5 and the pawl 40 do not mesh with each other and do not transmit torque.

On the other hand, the load on the rotor 24 increases due to the fish being caught.
When a certain amount of torque is applied, the handle [
High-speed gear 10.14 rotatable relative to N12 and shaft side member 8.12.16 non-rotatable relative to handle shaft 2
A slip occurs between the handle shaft 2 and the high speed gear 10, 15 through the friction plates 9, 13, 15, and only a certain amount of torque is transmitted from the handle shaft 2 to the high speed gear 10, 14, and no further torque is transmitted. In this state, the main gear 7 will no longer be rotated faster than the handle shaft 2 as it would be when no fish is hooked, so the electric train 5 and the pawl 40 will mesh, and this time, the gear 7 will rotate from the handle shaft 2 to the handle shaft 2. Power is mainly transmitted to the rotor 24 via the low-speed power transmission path, that is, the electric train 5, the pawl 40, the main gear 7, and the pinion 23a.

The two-stage gear 28 is driven by the high-speed gear 10.14 when the gear is not engaged, as described above, but is driven by the spur gear 7b of the main gear 7 when the gear is engaged. In either case, the rotation of the two-stage gear 28 is converted into a linear reciprocating motion of the spool @ 25 by the groove of the crank constituted by the eccentric pin 29 and the crank guide 30, so that the rotation of the two-stage gear 28 and the rotation of the rotor 24 In parallel, the spool 26 performs a linear reciprocating motion together with the spool shaft 25.

Now, as mentioned above, in the high-speed power transmission path, the gear ratio or speed ratio of the gear train consisting of the high-speed gears 10, 14, 2-stage gear 28I3, and the spur gear 7a of the main gear 7 is set to a. Since the gear ratio or speed ratio between the face gear 7a of the remaining main gear 7 and the pinion 23a is b, the gear ratio or speed ratio of the high-speed power transmission path is a.
xb (a>1>. Also, the gear ratio or speed ratio of the low-speed power transmission path is b, so the high-speed power transmission path has a larger gear ratio or speed ratio than the low-speed power transmission path. .

Therefore, with this reel, when the fish is not dead, the rotor 24 can be rotated at high speed with a large gear ratio or speed ratio using the high-speed power transmission path to quickly reel in the line. If this happens, the gears can be automatically changed and a larger force can be generated using a smaller gear ratio or speed ratio in the low-speed power transmission path.

Roughly speaking, in this embodiment, the threshold value of torque for performing the automatic shift can be adjusted as follows.

That is, when the adjustment knob 21 is rotated, this knob 2
1, the adjusting member 19 also rotates and moves in the axial direction, thereby increasing the force of the spring 20, and thus the shaft side members 8, 12, 16, friction plates 9, 11, 13, .
15 and the high-speed gears 10 and 14 change. Therefore, by rotating the adjustment knob 21, it is possible to adjust the torque threshold for performing the automatic gear shift.

Furthermore, in this embodiment, when the adjustment knob 21 is rotated, the convex portions 22a of the leaf spring 22 are sequentially engaged and disengaged from each @21d provided on the knob 21, so that the knob 21 is rotated in an articulated manner. . Therefore, the adjustment knob 21 does not move spontaneously against the angler's will, and the valley groove 21
If one knob corresponding to d is provided on the knob 21, the adjustment knob 21 can be stopped at each scale, and these one
It is possible to easily understand the magnitude of the torque threshold value from the demand.

Furthermore, if the reel is used for a long period of time, the friction plate 9
, 11, 13, 15, etc., the torque threshold value deviates from the initial setting value for the same rotational position of the adjustment knob 21 with respect to the main body 1. However, in this embodiment, after the adjustment knob 21 is pulled back in the axial direction from the adjustment member 19 to disengage the toothed recess 21G and the tooth 19e, the adjustment knob 21 is moved back from the adjustment member 19 in the relative position from the previously engaged position. The angler can easily adjust the torque threshold for the same rotational position of the adjustment knob 21 relative to the main body 1 by fitting the toothed recess 21C and the tooth 19e again at a position rotated by a necessary amount in the direction. Can be done.

FIG. 7 shows another embodiment of the invention. In this embodiment, boss portions id and ``le'' are provided at opposing positions on both sides of the reel body 1, respectively, and the handle shaft 2 is attached to the main body 1 at these boss portions 1d and Ie. The handle lNl is inserted into the handle in a rotatable state.
A handle 3 is coupled to one end of the handle 2.

A boss 1d is provided on the flat surface portion 2CKU of the handle shaft 2.
In order from the side toward the side 1e, the shaft side member 8, the friction plate 9, the high speed gear 10. Friction plate 11, shaft side member 12, friction plate 13
, a high-speed gear 14, an annular gear holder 50, and an annular clutch holder 51 are mounted adjacent to each other.

The shaft side members 8, 126 and the clutch presser 51 can move in the axial direction with respect to the handle shaft 2, but cannot rotate (however, the shaft side member 8 is
2, it cannot move any further toward the post 1d side of the main body 1).

The friction plates 9, 11, 13, the high-speed gear 10.degree. 14, and the gear presser 50 are movable in the axial direction and rotatable relative to the handle shaft 2.

A male thread 2d is cut near the end of the handle shaft 2 on the boss 1e side, and a spring retaining nut 52 is screwed into the male thread 2d. A compression coil spring 20 is interposed between the spring retainer nut 52 and the clutch retainer 51, and this spring 20 biases the clutch retainer 51 toward the boss 1d. A female thread 1f is cut on the outer end side of the boss 1e of the main body 1, and a cap 54 is screwed into this female thread 1f. This cap 54 has a hole 54e in its center, and the end of the handle 3 passes through the hole 54e.

Other windmills 5, claws 40. Main gear 7, pinion 23a,
The configurations of the rotor 24, spool shaft 25, spool 26, eccentric pin 29, crank guide 30, etc. are the same as in the previous embodiment.

In this embodiment, the shaft side members 8, 12, high speed gears 10.14, friction plates 9, 11.13, springs 20, gear holder 50. Clutch retainer 51 and spring retainer nut 52
etc. constitute a torque limiter means, and automatic gear shifting is performed in accordance with fluctuations in the load applied to the rotor 24 in the same manner as in the previous embodiment.

Further, in this embodiment, when the spring retaining nut 52 is rotated, this nut 52 moves in the axial direction, which causes the force of the spring 20 to be applied to the shaft side members 8, 12, the friction members 9, 11, 13J5, etc. and the frictional force acting between the high-speed gears 10 and 14 changes.

Therefore, by rotating the nut 52, it is possible to adjust the torque threshold for performing the automatic gear shift.

FIG. 8 is a block diagram showing a power transmission path according to another embodiment of the present invention.

In this embodiment, the handle shaft 2 includes a shaft side member 79,
Friction plate 80. It is connected to the rotor 24 via the high-speed gear 81 and pinion 23a, and is also connected to the one-way clutch means 104, the low-speed gear 82, and the pinion 23af8.
- connected to the rotor 24 via.

Hey, shaft side member 79, friction plate 80. The high-speed gears 81 are engaged and suppressed from each other, as in each of the embodiments described above. Further, the high speed gear 81 and the low speed gear 82 are meshed with the pinion 23a.

The gear ratio or speed ratio (rotational speed of pinion gear 23a/rotational speed of high-speed gear 81) between high-speed gear 81 and pinion 23a is the same as that of low-speed gear 82 and pinion 23a.
38 (rotational speed of pinion 23a/rotational speed of low-speed gear 82).

In this embodiment, the pinion 23a constitutes the first power transmission path, while the low speed gear 82 and the pinion 23a constitute the first power transmission path.
3a constitutes the second power transmission path. Similarly to the above embodiments, when there is no fish on the hook, power is transmitted from the handle @lI2 to the shaft side member 79, the friction plate 80, the high speed gear 81, and the pinion 23a. While the line is wound up at high speed, when a fish is hooked, the line is mainly moved from the handle shaft 2 to the one-sided clutch means 1.
04, the low-speed gear 82, and the pinion 23a, and a large force can be generated.

Note that the torque limiter means and one-sided clutch means according to the present invention are not limited to those configured as in each of the embodiments described above, and other configurations that achieve the same functions may also be used. .

(Effects of the Invention) As described above, the spinning reel according to the present invention has the excellent effect of automatically switching the gear ratio or speed ratio depending on whether a fish is caught or not. be.

[Brief explanation of the drawing]

FIG. 1 is a partial cross-sectional view showing an embodiment of a spinning reel according to the present invention, FIG. 2 is a cross-sectional view taken along the line ■-■ in FIG. 1, and FIG. 3 is a cross-sectional view taken along the line ■-■ in FIG. 4 is a sectional view taken along the line IV--IV in FIG. 1, FIG. 5 is a sectional view taken along the line V-V in FIG. 1, and FIG. 6 is a block diagram showing the power transmission path of the above embodiment. 7 is a partial sectional view showing another embodiment of the present invention, FIG. 8 is a block diagram showing a power transmission path of another embodiment of the present invention, and FIG. 9 is a conceptual diagram showing the present invention. The block diagram shown is as follows. DESCRIPTION OF SYMBOLS 1... Reel body, 2... Handle shaft, 5... Windmill, 7... Main gear, 7a... Face gear, 7b...
... Spur gear, 8.12.16.79 ... Shaft side member, 9
．． 11.13.15...Mairyo board, 10, 14.81
...High speed gear, 23a...Pinion, 24...
Rotor, 28... 2-stage gear, 28a... Small gear, 2
8b...Large gear, 40...Claw, 52...Spring retainer nut 1~. 82...Low speed gear, 101...First power transmission path, 102...Second power transmission path, 10
3... Torque limiter means, 104... One-way clutch means.

Claims (1)

[Scope of Claims] A handle shaft and a rotor, each rotatably supported by a reel body, a first power transmission path and a second power transmission path each having an output end connected to the rotor,
Torque limiter means is interposed between the handle shaft and the input end of the first power transmission path and does not transmit torque exceeding a predetermined value, and between the handle shaft and the input end of the second power transmission path. and a one-way clutch means for transmitting torque in only one direction, the handle shaft being rotated in the normal direction, and the input side and the output side of the torque limiter means being rotated integrally. If so, the rotational speed of the input end of the second power transmission path is higher than the rotational speed of the input side of the one-way clutch means, and the rotational speed of the input end of the second power transmission path is higher than the rotational speed of the input side of the one-way clutch means. The speed ratio of the high-speed power transmission path (rotor rotational speed/handle shaft rotational speed) from the handle shaft to the one-way clutch means and the second A spinning reel characterized in that the speed ratio is greater than the speed ratio of a low-speed power transmission path that reaches the rotor via the power transmission path.