JPS5949817B2 - reciprocating electric razor - Google Patents

Description

[Detailed description of the invention] The present invention relates to a reciprocating electric razor.

Conventionally, in this type of reciprocating electric razor, an eccentric element having an eccentric pin is fixed to the output shaft of a drive motor, and the upper plate of the driver element, which is rectangular when viewed from the side, is connected to the eccentric pin. An inner cutter stand for holding an inner cutter is connected to the drive element so that the inner cutter is reciprocated on the inner surface of the outer cutter.

However, in the conventional configuration, when the drive element connected to the eccentric pin swings, vibration occurs, resulting in significant noise and the like.

In addition, since the lower plate of the rectangular driver when viewed from the side follows the upper plate that is directly connected to the eccentric pin, the upper and lower plates are not driven completely parallel, resulting in insufficient force transmission and sharpness. It was declining.

The present invention eliminates the above-mentioned drawbacks and can sufficiently reduce noise,
Another object of the present invention is to provide a reciprocating electric razor that can adjust the cutting direction.

The present invention will be explained below along with the drawings.

1 to 3 show an embodiment of the present invention. In the figures, 1 is a housing in which a drive motor 2 is housed, and the output shafts of the drive motor 2 have a mechanical phase of 1.
An eccentric cam 4 with an eccentric pin 3 projecting upward in a manner that is offset by 80 degrees is fixedly provided.

A driver 5 is connected to the eccentric pin 3 and the eccentric cam 4 so as to be able to reciprocate.

a lower drive plate portion 7 in which a through hole 6 is bored approximately in the center of the drive element 5;
The first elastic plate parts 8, 8 are connected to the lower drive plate part 7 via a pair of vertical thin first elastic plate parts 8, 8.
A lower drive plate portion 9 that forms an inverted U-shape is integrally connected to the lower drive plate portion 9.

Further, on the upper surface of the lower drive plate portion 7, a lower drive arm 10 is provided protrudingly provided at its tip into which the eccentric cam 4 passing through the through hole 6 can be inserted.

The lower drive arm 10 includes a base 11 bent in an L-shape in a direction perpendicular to the lower drive plate 7 and a tip 12 bent in an L-shape in a horizontal direction with respect to the base 11. ing.

Further, the connecting portion 13 between the base portion 11 and the tip portion 12 has sufficient flexibility, and the free end of the tip portion 12 is formed as a ring-shaped portion 14 so that the eccentric cam 4 can be inserted thereinto. It reaches above the through hole 6.

On the other hand, the lower drive arm 1 is provided on the lower surface of the lower drive plate portion 9.
An upper drive arm 15 is provided above the drive arm 15 and protrudes from the upper drive arm 15 into which the eccentric pin 3 can be engaged.

The upper drive arm 15 is formed in an E-shape, and has side leg parts 16, 1 bent in an L-shape in a direction perpendicular to the lower drive plate part 9.
6, and a central leg portion 18 integrally connected to the side leg portions 16, 16 and formed as a ring-shaped portion 17 at its protruding end so that the eccentric pin 3 can be inserted therein.

Further, a driving rod portion 20 having a socket 19 is erected at the center of the upper surface of the lower driving plate portion 9 .

Furthermore, the first elastic plate portions 8 are provided at both ends of the lower drive plate portion 7.
. ing.

Further, mounting ears 23, 23 are extended from the extension ears 22, 22, and by inserting screws 24, 24 through the screw holes and screwing the screws 24.24 into the housing 1, the drive element itself It is provided so that it can be attached to the housing 1.

Reference numeral 25 denotes an inner cutter base whose support shaft portion 26 is received in a socket 19 provided in the drive rod portion 20 of the drive element 5, and which is connected to the drive element 5. The inner cutter group 27 is held therein, and the inner cutter base 25 is supported by a suitable spring. The inner cutter group 27 is configured to slide on the inner surface of the outer cutter 28 when the drive element 5 is driven once.

The outer cutter 28 is supported by an outer cutter frame 29, and the outer cutter frame 29 is attached to the housing 1 by engaging an elastic support pin 30 attached to the housing 1.

It is loaded onto Group 1.

Furthermore, the operation of the above embodiment will be explained in detail.

When the drive motor 2 is now driven, the eccentric cam 4 is engaged with the annular portion 14 provided on the lower drive arm 10 of the lower drive plate portion 7, and the eccentric cam 4 is engaged with the ring portion 14 provided on the lower drive arm 15 of the upper drive plate portion 9. The annular portion 17 has a phase of 180 degrees with respect to the eccentric cam 4.
Since the eccentric pins 3 provided at different degrees are engaged, a motion component acting in a direction perpendicular to the sliding direction of the inner cutter group 27 is applied to the connecting portion of the lower drive arm 10 ] 3 or the upper drive arm 15 The lower driving plate part 7 and the lower driving plate part 9 reciprocate in opposite directions.

Therefore, the vibrations generated in the lower drive plate portion 9 to which the inner cutter stand 25 is connected are the vibrations generated in the lower drive plate portion 7, which reciprocates in the opposite direction to the lower drive plate portion 9, with a mechanical phase difference of 180 degrees. In other words, the vibrations generated in the lower drive plate part 9 are canceled out by the reciprocating motion of the lower drive plate part 7, and the lower drive plate part 7 functions like a parallelism with respect to the lower drive plate part 9, so that the vibrations are canceled out. It is greatly reduced.

Also, at this time, the thin first elastic plate parts 8, 8 and the second elastic plate parts 21, 21 have sufficient flexibility, and the driver element is moved from the position shown in FIG. 4 to the position shown in FIG. When swinging, the first elastic plate parts 8.8 and the second elastic plate parts 21 are more flexible than when the first elastic plate parts 8, 8 and the second elastic plate parts 21, 21 do not have flexibility. .21 works to expand, the displacement amount δ in the vertical direction with respect to the reciprocating motion of the driver (driver element) can be reduced, and remote causes such as vibration can also be reduced in this respect.

FIGS. 6 to 9 show other embodiments of the present invention, and in this embodiment, compared to the above-described embodiment shown in FIGS. 1 to 5, In order to further effectively reduce vibration, a through hole 6 is formed on the upper surface of the lower drive plate portion 9a.
Balance bodies 31a, 31a are fixedly installed on both sides of a, that is, near the inside of the first elastic plate parts 8a, 8a.

In other words, ``comparing the mass term of the lower drive plate part 9a to which the inner cutter stand 25a holding the inner cutter group 27a that is in pressure contact with the outer cutter 28H and the mass term of the lower drive plate part 7a, the lower drive plate part 7a is generally lower. Since the mass term of the lower drive plate portion 9a is larger than the mass term of the plate portion 7a, the balance bodies 31a, 31a such that both mass terms are substantially equal are attached to the lower drive plate portion 9a with a small mass term. Attached.

In addition, to explain in detail, the mass of the inner cutter group 27H is M, the balance body 3
1a is m, the mass of lower drive plate portion 7a including the mass of lower drive arm 10a is ml, and the mass of lower drive plate portion 9a including the mass of upper drive arm 15a and drive rod portion 20H is m2.
, when the amount of movement of the lower drive plate 7a is al, the amount of movement of the lower drive plate 9a is a2, and the rotation speed of the drive motor 2a is ω,
The inertial mass of the lower drive plate portion 7a including the mass of the balance body 31a is (m1+m)al・ω2 (1), and the inertial mass of the lower drive plate portion 9a is (M10m2)δ2・ω2・...(2), and if we find the mass of the balance body 31a, (1)=
(2) That is, (m1+m)al・ω2 = (M10m2)δ2・ω2
(m1+m) a1= (M+m2) δ2・(3)
Therefore, from the above formula (3), m = (M0m2) -ml +++++・+
++・++++・+ (4)1 Therefore, if the balance body 31a satisfying the formula (4) is attached to the lower drive plate portion 7a, the vibration of the lower drive plate portion 9a will be reduced compared to the embodiments shown in FIGS. 1 to 5. can be further reduced.

Other configurations and operations are similar to those of the above-described embodiment.

FIG. 10 shows yet another embodiment of the present invention,
In this embodiment, unlike the embodiments shown in FIGS. 6 to 9, a balance body is not provided, and in order to further reduce vibrations occurring in the lower drive plate, the output of the drive motor 2b is adjusted to the eccentric cam 4b relative to the axis. Eccentricity, that is, movement amount a1 of the lower drive plate portion
is made larger than the eccentricity of the eccentric pin 3b with respect to the output axis of the drive motor 2b, that is, the movement amount a2 of the lower drive plate portion.

In other words, as mentioned above, the mass term of the lower drive plate section is generally larger than the mass term of the lower drive plate section, so the lower drive plate section with a smaller mass term should be set so that both mass terms are substantially equal. By making the movement amount a1 larger than the movement amount a2 of the lower drive plate portion, the inertial mass term of the lower drive plate portion is increased.

To be more specific, in the above equation (3) explained in accordance with the embodiment shown in FIGS. 6 to 9, when the balance body is not added as in the same embodiment, the mass M of the inner cutter group, the lower drive plate part mass m
1. The relationship among the mass m2 of the lower drive plate, the movement amount a1 of the lower drive plate, and the movement amount a2 of the lower drive plate is ml·al−(M0m2)δ2, and therefore.

On the other hand, since usually 'M+'''-≧1l, al) -8-1, therefore, al≧a2 2, and especially assuming the relationship al>δ2, the above (5)
If the ratio between the moving amount a1 of the lower driving plate and the moving amount a2 of the lower driving plate is determined so as to satisfy the equation, vibrations occurring in the lower driving plate can be effectively reduced.

Other configurations and operations are similar to those of the above-described embodiment.

FIG. 11 shows still another embodiment of the present invention,
In this embodiment, the lower drive plate part is configured to reciprocate completely parallel to the lower drive plate part of the driver 5c.

A first elastic plate that integrally connects the lower drive plate portion 9C to the lower drive plate portion 7C from the length Ll of the second elastic plate portions 21C and 21C having extension ears 22C and 22C fixed to the housing. The length L2 of the portion 8C58C is set to be large.

In this case, unlike the embodiments shown in FIGS. 1 to 5, the second elastic plate parts 21C, 21C are erected inside the first elastic plate part 8C58C, and extended to the upper ends of the second elastic plate parts 21C, 21C. 2. The extended ears 22
C, 22C into the through hole 32C of the first elastic plate portion 8C58C,
It extends from 32C and can be fixed to the housing.

Therefore, to look at the conditions under which the lower drive plate part 7C completely reciprocates with respect to the lower drive plate part 9C of the driver element 5c with particular reference to FIG. The length of the elastic plate portion 8C is L2, and the displacement angle of the second elastic plate portion 21C is δ1.
, when the displacement angle of the first elastic plate portion 8C is δ2, the amount of movement of the lower drive plate portion 7C is al, and the amount of movement of the lower drive plate portion 9C is δ2, al=L1Sinθ1・(6) a2=L2Sinθ2 al・...(7), and the vertical displacement amount of each of the lower drive plate part and the lower drive plate part is δ1
, δ2, al -Ll(1-cosθ
1) δ2=L2(1-CO8θ2).

Therefore, if δ1=δ2, the lower drive plate portion and the lower drive plate portion will reciprocate completely in parallel, and it is sufficient to satisfy equation (8).

On the other hand, to find the value of L1/L2, it can be said that a1/a2 = A. Therefore, when A=1, 11 24 In other words, the movement amount a1 of the lower drive plate part 7C and the movement amount of the lower drive plate part 9C. If the ratio a1/a2 with a2 becomes large, the second elastic plate part 2
Ratio L between length Ll of 1C and length L2 of first elastic plate portion 8C
l/L becomes large and approaches 1 infinitely,
In the limit, when a2=0, L]/L2=1.

Therefore, if we organize this, a I
If L 1 1-ku1, then 0〈-〈-・・・・・・
(9) a 2 L 2 4al
I Ll If part 1, -ku-〈1 ...... (10)
24-L2 Therefore, in order to reciprocate the lower drive plate portion 7C and the lower drive plate portion 9C in mutually opposite directions and to eliminate vertical displacement of the lower drive plate portion 9C, the above (8) is particularly required. , (9)
, (10), the configuration may be such that the relationship Ll<L2 is always satisfied.

Other configurations and operations are similar to those of the above-described embodiment.

In addition, the embodiment of FIG. 11 is slightly different, and as shown in FIG. 13, the lower drive plate portion 9d is erected inside the first elastic plate portion 8d that is integrally connected to the lower drive plate portion 7d. The second elastic plate portion 21d has substantially the same effect as the embodiment shown in FIG. 11 even if the mounting ear piece 23d is directly fixed to the housing without passing the extension ear portion through the first elastic plate portion. be able to.

According to the reciprocating electric razor of the present invention configured as described above, the driver reciprocates in a well-balanced state when it swings, thereby suppressing the generation of vibration and noise. Since it is possible to greatly reduce the amount of force and to realize completely parallel reciprocating motion of the drive element, it is possible to achieve remarkable effects such as good transmission of driving force and improved cutting quality.

[Brief explanation of drawings]

Fig. 1 is a front view showing a part of an embodiment of the reciprocating electric razor of the present invention in cross section, Fig. 2 is an enlarged perspective view of the same part, and Fig. 3 is the same as seen from the opposite direction of Fig. 2. Partially enlarged perspective view, 4th
5 and 5 are explanatory diagrams of the same operation, FIG. 6 is a front view showing a cross section of a part of another embodiment of the present invention, FIG. 7 is an enlarged perspective view of the same part, and FIGS. 8 and 9 are FIG. 10 is an explanatory diagram of another embodiment of the present invention, FIG. 11 is a partially enlarged perspective view of still another embodiment of the present invention, FIG. 12 is an explanatory diagram of the same,
FIG. 13 is a partially enlarged perspective view of another embodiment of the present invention. 1... Housing, 2, 2b... Drive motor, 3.3b... Eccentric pin, 4, 4b...
...Eccentric cam, 5.5C...Driver, 6,
6a...Through hole, 7,7a, 7C,7d...
--Lower drive plate section, 8. 8a, 8C58d...
...first elastic plate part, 9. 9a, 9C, 9d...
...Lower drive plate part, 10, 10a...Lower drive arm, 11...Base, 12...Tip part, 13...Connection part , 14... ring-shaped portion, 15, 15a... lower drive arm, 16...
... Side leg part, 17... Annular part, 18...
...Central leg, 19... Socket, 20, 20a.
... Drive rod section, 21, 21C, 21d...
・Second elastic plate part, 22, 22C... extension ear part,
23... Mounting ear piece, 24... Screw, 2
5, 25a... Inner cutter stand, 26... Support shaft portion, 27, 27a... Inner cutter group, 28° 28a.
...Outer blade, 29...Outer blade frame, 30
...Elastic support pin, 31a...Balance body, 32C...Through hole.

Claims (1)

[Scope of Claims] 1. An electric razor in which the output of a drive motor housed in a housing is transmitted to an inner cutter via an eccentric element and a drive element, and the inner cutter is reciprocated on an inner surface of an outer cutter. An eccentric cam that is fixedly attached to the output shaft and has an eccentric pin protruding with a mechanical phase shifted by 180 degrees, and a lower drive plate part are integrally connected to the lower drive plate part via a first elastic plate part, and the housing and a drive element having a second elastic plate portion fixed to the lower drive plate portion and a drive arm provided on each of the lower drive plate portions and a drive arm that engages with an eccentric cam and an eccentric pin. 1. A reciprocating electric razor according to claim 1, wherein a balance body is attached to the lower drive plate portion. 3. The reciprocating electric power saw according to claim 1, in which the amount of eccentricity of the eccentric cam with respect to the output axis of the drive motor is greater than the amount of eccentricity of the eccentric pin with respect to the output axis of the drive motor. 4. First elasticity The reciprocating electric power mister according to claim 1, wherein the length of the plate portion is greater than the length of the second elastic plate portion.