EP2066260A1

EP2066260A1 - Electric toothbrush, and transmission for an electric toothbrush

Info

Publication number: EP2066260A1
Application number: EP07725049A
Authority: EP
Inventors: Franz Fischer; Armin Bärtschi; Christian Hilfiker
Original assignee: Trisa Holding AG
Current assignee: Trisa Holding AG
Priority date: 2006-09-29
Filing date: 2007-05-10
Publication date: 2009-06-10
Also published as: CN101516290A; CA2663600A1; EP2272463A2; WO2008040401A1; CA2842985A1; JP5348592B2; US20180228583A1; EP3610830A1; US9968427B2; EP2272463A3; JP2010504775A; EP2548531A3; US20150289958A1; CA2842985C; US9572642B2; US20170189151A1; DE202007019478U1; EP2548531A2; US8365335B2; US20130097789A1

Abstract

The transmission (48) according to the invention for an electric toothbrush serves to transmit and convert a rotation movement from an electric motor (58) into a particularly gentle and effective cleaning movement of a cleaning element (40). The ratio of the distance between the longitudinal centre axis of a drive shaft (30) and the longitudinal centre axis of a drive shaft (60) of the transmission (48) and of the distance between the longitudinal centre axis of a shaft (60, 78) driving a cam (72) of the transmission (48) and of the longitudinal centre axis of the cam (72) is at least 10:1.

Description

Electric toothbrush and gear for an electric toothbrush

The present invention relates to a transmission for an electric toothbrush according to the preamble of claims 1 and 23 as well as an electric toothbrush according to claims 8 and 24.

Electrically operated toothbrushes, so-called electric toothbrushes, which have electric motors for driving cleaning elements arranged on them, are generally known at the present time. In this case, the cleaning elements attached to brush heads are typically pivotally moved by means of a reduction of a rotational movement provided by the electric motor via a reducing gear. Depending on the form of movement which carries out the cleaning element about an axis associated with it, a distinction is made between reversing pivoting, reversing translational and combined movements, which auf'eisen both reversing pivoting and reversing translational motion components.

An electric toothbrush with a reversibly pivotable cleaning element is disclosed, for example, in US Pat. No. 3,104,409. The electric toothbrush described therein has a base body with an electric motor accommodated therein, the rotational movement of which is converted into a reversingly pivoting movement of an output shaft by means of a transmission. On the output shaft, a handle-like brush head is attached, which has a cleaning element equipped with bristles in the head end region. The cleaning element together with the entire brush takes place in the attached state of the electric motor - that is, in an active Operating state - a reversing pivoting movement about the output axis extending substantially parallel to the longitudinal axis of the brush attachment.

Another electric toothbrush is described in CH 688537. This electric toothbrush also has an electric motor arranged in a body designed as a handle, which, in the active operating state, provides a rotational movement which is converted by means of a gear into a reversingly pivoting movement of an output shaft. Also in this case, a brush head with a arranged on the head area bristle-occupied cleaning element can be plugged onto the base unit. A movable in the brush attachment axle extension with a deflecting converts by an end-side engagement of the deflection in a guide slot of the cleaning element bearing hub the pivotal movement of the output shaft in a reversing pivotal movement of the cleaning element. The cleaning element associated with the pivot axis extends at right angles to the output axis. The reversing pivotal movement of the substantially circular disc-shaped hub with the cleaning element attached thereto is also referred to as a reversibly rotating or reversing oscillating movement.

An electric toothbrush, in which, in the active operating state, a cleaning element arranged on a brush attachment carries out a reversing translatory reciprocating movement is disclosed, for example, in EP-A-1639914. It is by means of a thrust crank-type transmission between a drive axle of an electric motor and a driven-side push crank the entire Brush head reciprocated parallel to its longitudinal axis.

In US 5,321,865 an oral hygiene device, in particular an electric toothbrush is described, arranged on a brush attachment cleaning element in the active operating state performs a combined movement, which consists of a reversing pivotal movement about a driven axis which is substantially parallel to the longitudinal axis of the brush attachment, and a reversing translational reciprocating motion of the output shaft in the direction of the longitudinal axis of the brush attachment composed. A used here for reaching gear has two eccentrically arranged on a gear cam, which converts the rotational movement provided by the electric motor in the attached state in the two components of motion, on the one hand reversing pivoting and on the other hand translationally reciprocating, and transmits via a pickup on the output shaft , Due to the specific geometric design of the two cams, the two components of motion oscillate at the same frequency as is predetermined by the gear on which they are fixed.

Other embodiments of electric toothbrushes with integrated gears are for example in the

GB 1,134,158, US 2004/0158944, FR 1,341,439 and WO 03/070122.

Additional details on the design of brush heads and cleaning elements can be found inter alia in the publications DE-A-19727018, DE-A-4228859 and EP-A-1532891. Object of the present invention is therefore to provide a transmission and associated movement for the output shaft or the associated cleaning element of an electric toothbrush or an electric toothbrush with such a transmission, by which it is possible, a gentle for the gums, particularly effective Provide cleaning movement of the cleaning elements in a cost-effective manner.

This object is achieved by a transmission for an electric toothbrush according to claim 1 and an electric toothbrush according to claim 8. Particularly preferred embodiments are equipped with the features listed in the dependent claims.

The transmission according to the invention for an electric toothbrush serves to transmit and transform a rotational movement, which is provided by an electric motor on a drive axle, into a movement of an output shaft, which in turn is intended to drive a movable cleaning element of the electric toothbrush.

For this purpose, the transmission has a preferably eccentrically with respect to its driving axis rotatably arranged cam and a corresponding, with the output shaft rotatably connected to customers. In order to injure the gums as little as possible and at the same time to achieve a very good cleaning effect, the output shaft and the cleaning element connected to it performs a preferably fast movement with a small deflection. In order to provide the required small deflection, so the required small deflection angle on the customer or on the output shaft, is According to the invention, the ratio of the distance from the longitudinal central axis of the output shaft to the longitudinal center axis of the drive axle in the region of the pickup to the distance between the longitudinal center axis of the cam driving axis and the longitudinal center axis of the cam at least 10: 1. The speed of the movement is achieved, for example, by using an electric motor, which provides a high speed between 2000 rpm and 12000 rpm in unloaded operation.

The eccentric gear formed in accordance with the invention has a relatively simple structural design and is equipped with a plurality of components which are preferably to be processed by injection molding, which permits a particularly cost-effective production overall.

A further object of the present invention is to provide a transmission and an associated movement sequence for the output shaft or the associated cleaning element of an electric toothbrush or an electric toothbrush with such a transmission, by which it is possible for the manufacturer, provided by an electric motor continuous rotational movement in one direction of rotation in a simpler, more cost-effective and more flexible way to better match the desired cleaning movement of a cleaning element of the electric toothbrush. The movement of the cleaning element should preferably allow a laterally reversing pivoting movement and / or a translational reciprocating movement in the axial direction of the output shaft in all transmission variants. A further object of the invention is to provide a brush adapted optimally for the corresponding embodiment of the transmission. In particular, it is about the formation of an advantageous connection between the brush head and the brush head and the output axis for generating an optimal sequence of movements. Overall, the invention is intended to provide the desired movement of the cleaning element via an inventive chain of action electric motor - transmission - output shaft - Aufsteckmechanismus brushhead - cleaning element - bristles available.

This object is achieved by a transmission for an electric toothbrush according to claim 23.

The inventive transmission, which is the conversion of a continuous rotational movement in a rotational direction, which is provided by an electric motor on its drive axle, in a movement for driving a cleaning element is formed in a variant embodiment as a multi-stage transmission. It has at least one drive-side first gear stage and at least one output-side second gear stage, wherein at least one gear stage is designed as a reduction and at least one gear stage as a translation. In this way, it is ensured that the movement forwarded by the multistage transmission with respect to speed and torque manufacturer can be easily and flexibly adapted on the one hand to the specifications of the electric motor and on the other hand to the desired movement properties of the cleaning element. In a further embodiment, the gear ratio is equipped with a cam and a cam extension, which make it possible to provide both a reversing pivoting movement component and a reversing translational movement component or a combination of the two for the output axis and thus for the cleaning element. By adapting the geometry and the arrangement of the cam and the cam extension, a variety of novel, particularly effective plaster movement pattern of the output shaft and thus also of the cleaning element can be generated.

Another object of the present invention is to provide an electric toothbrush with a transmission in which the transmission allows a structurally simple, low-noise and freely predeterminable motion transmission.

This object is achieved by an electric toothbrush according to claim 24.

This electric toothbrush according to the invention is equipped with a base body which forms a handle and accommodates an electric motor and a transmission, a neck adjoining the base body and a head arranged opposite the neck on the neck. At the top of a connected to an output shaft, movable cleaning element is arranged. The transmission has a cam and a pickup operatively connected to the output shaft. The cam preferably has a cross section in the form of a circle or a rounded n-corner, where n is an odd positive number. In the transmission of a movement of the cam on the customer by means of sliding tap gear ratios can be realized equal and especially greater than 1: 1 due to the specific cross-sectional shapes of the cam. In addition, the structure of the transmission is relatively simple and due to the sliding tap it comes in the active mode only to a low noise.

Some particularly preferred embodiments of the inventive transmission or the inventive electric toothbrush are described in detail below with reference to a drawing. The figures of the drawing show in detail:

1 is a perspective view of a designed as a handle body of a

Electric toothbrush with a tapered end portion from which protrudes an output shaft on which a brush attachment shown in Figure 2 can be plugged.

2 shows a perspective view of an electric toothbrush with the base body shown in FIG. 1 and a brush attachment plugged onto the output shaft with a bristle-mounted cleaning element;

3 shows a perspective view of a further embodiment of the main body of the electric toothbrush according to the invention with a spigot shaft side in the conical end region arranged on the spigot for rotationally fixed Recording a shown in Figure 4, another embodiment of the brush attachment.

4 shows a perspective view of an inventive electric toothbrush with the base body shown in FIG. 3 and an attached brush head with a reversibly oscillatable cleaning element;

Fig. 5 in a side view of a part of the inner life of the inventive electric toothbrush, including a

Including inner frame, which is received in a base body shown in Figures 3 and 4 and in which an electric motor with a drive axle and a transmission according to the invention are arranged with the output shaft.

6 is a perspective view of a translation of the inventive transmission with a crown wheel, on which a cam is arranged, which is scanned by a fixedly connected to the output shaft, clamp-shaped consumer.

FIG. 7 is a perspective view of the pickup shown in FIGS. 5 and 6; FIG.

8 is a perspective view of the crown wheel with a cam of known geometry and arrangement.

Fig. 9 in a perspective view a part of an embodiment of the inventive Getriebes with the crown wheel, on the toothed side surface eccentrically with respect to the axis of rotation of the crown wheel, a triangular-shaped rounded cam is arranged;

10 is a perspective view of a part of another embodiment of the inventive transmission with a triangular cam which is arranged concentrically with respect to the axis of rotation of its associated crown wheel.

11 is a perspective view of part of a further embodiment of the transmission according to the invention with a pentagonally rounded cam mounted concentrically with respect to the axis of rotation of its associated crown wheel;

12 is a perspective view of another embodiment of the transmission of the invention with a crown wheel, on the toothed side surface of a cam and above the cam, a cam extension are arranged, both of which are scanned by the consumer;

Fig. 13 is a side view of the translation shown in Fig. 12;

14 is a perspective view of the crown wheel shown in FIGS. 12 and 13 with a triangularly rounded cam and a above the cam, eccentrically arranged with respect to the rotational axis of the crown wheel cam extension, which has a circular cross-section and is arranged eccentrically with respect to the axis of rotation of the crown wheel;

15 is a perspective view of another embodiment of the crown wheel with a pentagon-shaped rounded cam and an eccentrically mounted with respect to the axis of rotation of the crown wheel, triangular rounded cam extension.

FIGS. 16-19 show, in graphical representations, the deflection of the output axis as a function of time or the angle of rotation of the crown wheel for different ones, in each case to the left of the graphical ones

Illustrations given embodiments of cams;

Fig. 20 is a further graphical representation of the deflection of the output shaft for an adjacent embodiment of a

Cam with a cam extension to

Providing a combined form of movement with a reversing pivoting and a reversing translational

Movement component;

21 shows a perspective view, in particular a top view, of an embodiment of a brush-on brush body; FIG. 22 shows a perspective view, in particular a bottom side view, of the brush attachment body shown in FIG. 21; FIG.

FIG. 23 shows in a perspective view, in particular a top view, a brush attachment with the brush attachment body shown in FIG. 21 and FIG. 22; FIG.

FIG. 24 shows in a perspective view, in particular a bottom side view, the brush attachment shown in FIG. 23; FIG.

FIG. 25 shows a sectional view of the embodiment of a brush head with a bristle-tipped head shown in FIGS. 23 and 24;

FIG. 26 is a sectional view of another embodiment of a brush attachment with a reversibly oscillatable cleaning element already shown in FIG. 4; FIG.

FIG. 27 shows a perspective view, in particular a top view, of a further embodiment of a brush attachment, in which the cleaning element is arranged on a support shaft which can be moved in the interior of the neck; FIG.

FIG. 28 is a perspective view, in particular a bottom side view, of the brush attachment shown in FIG. 27; FIG. Fig. 29 in plan view the head of a brush attachment with respect to the neck movable and stationary cleaning elements;

Fig. 30 is a partial sectional view of the head of the brush head shown in Fig. 29;

Fig. 31 in a side view another

Embodiment of the head of the brush attachment with a movable relative to the neck and a stationary against the neck cleaning element;

Fig. 32 is a plan view of the top of the head of the brush head shown in Fig. 31;

33 shows in plan view the upper side of the head of a further embodiment of a brush attachment with bundles of bristles which protrude from elongated crescent-shaped base surfaces whose longitudinal extensions extend approximately in the longitudinal direction of the head;

34 shows in plan view the upper side of the head of a further embodiment of a brush head with bundles of bristles, which project from elongated, sickle-shaped base surfaces whose longitudinal extensions extend on the one hand approximately in the longitudinal direction of the head and on the other hand extend approximately in the transverse direction of the head;

FIGS. 35-38 in plan views different embodiments reversibly oscillatable Cleaning elements with different arrangements of bristle bundles;

Figs. 39-41 show in plan views of the tops of heads different embodiments of Figs

Brush heads with reversibly oscillatable cleaning elements and with respect to the neck stationarily arranged further cleaning elements;

42 shows in a perspective view a part of the inner life of a further embodiment of an inventive electric toothbrush with a single-stage gear, wherein the cam directly against rotation on the drive axle of the

Electric motor is attached;

FIG. 43 shows a side view of the inner life of the electric toothbrush according to the invention shown in FIG. 42; FIG.

44 shows a perspective view of the inner life of the toothbrush according to the invention, shown in FIGS. 42 and 43, without showing the inner frame;

FIGS. 45-48 show, in different views, a further pickup of the transmission for the embodiment of the electric toothbrush according to the invention shown in FIGS. 42 to 44;

Figs. 49a and 49b in a perspective view and a side view of a substantially cylindrical cambered cam intended to be eccentric with respect to a driving axis of the electric motor;

Fig. 50 is a perspective view of another embodiment of a cam having a rounded, substantially triangular cross-sectional shape;

51 shows in a diagram the dependence of the deflection angle of the output shaft on the rotational angle of the drive axle during a complete rotation of the drive axle using the cylindrical cam shown in FIG. 49;

52 is a diagram showing the functional relationship between the deflection angle of the output shaft and the rotational angle of the drive axle for the in

Fig. 50 shown cam having a substantially triangular, rounded cross-section.

FIG. 53 is a perspective view of the interior of another embodiment of the electric toothbrush according to the invention, in which the drive axle and the output shaft extend inclined relative to one another; FIG.

FIG. 54 is a further perspective view of the interior shown in FIG. 53; FIG. FIG. 55 shows, in a further perspective view, the inner life shown in FIGS. 53 and 54 without showing the inner frame; FIG. and

FIG. 56 shows a side view of the inner life shown in FIGS. 53 to 55 without showing the inner frame. FIG.

In FIGS. 1 to 4, main bodies 10 of electric toothbrushes 12 according to the invention are shown, onto which brush heads 14, which are shown for example in FIGS. 2 and 4, can be plugged. The main body 10 has an im

Essentially cylindrical outer contour and forms a handle 16 of the electric toothbrush 12. Along its longitudinal axis, the base body 10 in a lower

End region an erection section 18, an adjoining operating section 20 and an adjoining the actuating section 20

Aufsteckabschnitt 22, which is arranged at an opposite end portion of the Aufstellabschnitt 18, on.

The set-up section 18 serves for a safe installation of the electric toothbrush 12 on a solid base, for example a loading or base station. It comprises a bottom which is not visible in FIGS. 1-4 and which may be designed, for example, flat, with an erecting formation for accommodation in the loading or base station or with other functional formations.

The actuating portion 20 extends approximately over two-thirds of the total length of the base body 10 and is in the use of the electric toothbrush 12 substantially of the palm of a user enclosed. On an upper side 24 it is equipped with externally accessible, soft elastic material shaped actuators 26 for controlling operating conditions of the electric toothbrush 12, for example, on and off, a continuous or discrete adjustment of operating conditions or operating speeds, etc. equipped. In the actuating portion 20 are on the surface otherwise formed by a hard material soft elastic adhesive elements 28, which prevent slipping of the user's hand when using the electric toothbrush 12, respectively. In the embodiments of the basic body 10 shown in FIGS. 1 to 4, the actuating section 20 preferably tapers continuously in the direction of the attachment section 22.

The Aufsteckabschnitt 22 serves the mechanical coupling of the brush attachment 14 to the main body 10 of the electric toothbrush 12. It comprises in the embodiment of the base body 10 shown in FIG. 1 an end portion of an output shaft 30 and in the embodiment shown in FIG. 3 additionally a connection piece 32 for rotatably receiving the brush attachment 14.

The brush attachment 14 has a neck 34 whose free end region is predetermined for attachment to the slip-on portion 22 formed on the base body 10. The neck 34 is provided as a stick-like extension with a rounded cross-section smaller than that of the body 10. In the embodiment of the brush attachment 14 shown in Fig. 4 is at the top 24 of the neck 34 attached to an externally accessible actuator 36. The adjusting element 36 serves to select a pivoting range of a head 38 of the brush attachment 14 movable, in this embodiment, in particular reversibly rotatably arranged cleaning element 40th

The head 38 forms a free end region of the brush attachment 14 that adjoins the neck 34, generally widening in relation to the neck 34. It serves to receive or store cleaning elements 40, which are shown in FIGS. 2 and 4 Embodiments on the top 24 with bristles 42 and bundles of bristles 42 are occupied. On a not visible in FIGS. 2 and 4, the top 24 opposite bottom 44, the head 34 may also be preferably equipped, for example, with a tongue cleaner preferably made of soft material.

In the embodiment shown in Fig. 2 embodiment of the _invention, the electric toothbrush 12, the cleaning member 40 is fixed to the brush 14 and leads into an active operating state of the electric toothbrush 12, together with the entire brush 14 transmitted from the output shaft 30 reversing pivoting movement. In the embodiment of the electric toothbrush according to the invention shown in FIG. 4, the cleaning element 40 is mounted pivotably with respect to the head 38 and the neck 34. In the active operating state of the electric toothbrush 12, the cleaning element carries out a reversingly rotating movement about an axis which runs almost at right angles to the longitudinal axis of the neck 34. Although the resulting Movements of the cleaning elements 40 of the embodiments of the inventive electric toothbrush 12 shown in FIG. 2 and FIG. 4 are different from one another, both sequences of movements are based on a reversing pivoting movement of the output shaft 30.

Inside the main body 10 of the electric toothbrush 12, a so-called inner frame 46 is arranged. The inner frame 46 is shown in a side view of a portion of the interior of the electric toothbrush 12 in FIG. The illustrated part extends from the outermost, brush-side end of the output shaft 30 to about the longitudinal center of the actuating portion 20. On the inner frame 46, an inventive transmission 48, a drive unit 50 and a control unit 52 are arranged, the latter two in Fig. 5 only partially visible are.

The control unit 52 is partially disposed on the upper side of the inner frame 46 and includes a printed circuit board 54 having disposed thereon components and a switching element 56 for switching on and off of the active operating state of the electric toothbrush 12. The switching element 56 is corresponding to the actuating elements 26 which are accessible from the outside are arranged on the base body 10, formed. The actuating elements 26 are preferably formed of a soft elastic material and allow it to exert actuating forces on the switching element 56 when actuated.

The drive unit 50 comprises an energy store, not shown in FIG. 5, in the form of one or more Batteries or a rechargeable battery or a power supply, which is electrically connected to an electric motor 58, respectively. The electric motor 58 provides on its associated drive axle 60 a continuous rotational movement in a rotational direction through 360 °.

In an unloaded condition of the cleaning interaction, the rotational speed of the electric motor is - with connected gear 48 and plugged brush attachment 14 - between 1000 revolutions per minute (RPM) to 15000 U / min, preferably 3000 U / min to 8000 U / min 8000 rpm to 12000 rpm. By using motors with these high speeds, a high cleaning effect for this correspondingly fast moving cleaning elements 40 is made possible. The operating voltage for feeding the electric motor 58 is 1.3 V to 3 V, with a current flow in the above-defined unloaded operation between 300 mA to 1500 mA, preferably 400 mA to 1200 mA.

On the output side, the transmission 50 is followed by the transmission 48 according to the invention on the inner frame 46.

The transmission 48 transmits and converts the electric motor

58 provided on the drive axle 60, in

Essentially continuous rotary motion in a reversing movement of the output shaft 30. The invention described in detail by the following

Gear 48 provided on the output shaft 30

Movement can be a reversing pivoting

Movement about the longitudinal center line of the output shaft 30, a reversing translational back and forth movement in the direction of the output shaft 30 or a combined Movement be reversing pivoting and reversing translational motion components.

For sealing the arranged on the inner frame 46 components 48, 50, 52, 54, 56 and 58 against the ingress of liquids and solids in the base body 10 is on the output shaft side of the inner frame 46, a sealing groove 62 formed, in which a sealing O-ring 64 or a lip seal is inserted. The likewise formed on the inner frame 46 connecting piece 32 is, like the entire inner frame 46, made of a stable hard material and has a brush attachment notch 66 on the underside. This brush attachment notch 66 cooperates with a later described element on the brush attachment 14 and prevents unwanted removal of the brush attachment 14 from the base body 10. In addition, the connection piece 32 is provided with substantially parallel to the output axis 30 extending edges to - as already mentioned - a non-rotatable Arrangement of the brush attachment 14 on the body 10 to ensure.

For storage of the output shaft 30 on the inner frame 46, the inner frame 46 is provided on the output shaft side with a corresponding, not visible in the figures Achsausnehmung. The diameter of the Achsausnehmung is chosen so that the output shaft 30 can move freely translational and / or rotating therein, the penetration of liquids and solids but is largely excluded.

The transmission 48 comprises in addition to the visible in Fig. 5 drive gear 68, which rotatably on the drive axle 60 of the electric motor 58 is arranged, in particular in Fig. 6 well visible crown gear 70 with a toothed side surface arranged on the cam 72 and a particular shown in Fig. 7, with the cam 72 interacting customer 74. At the customer 74 is the Output shaft 30 rotatably disposed. The output shaft 30 is in turn rotatable and possibly also displaceable in a driven axle sleeve 75, which is visible in Fig. 6, stored. By attaching the output shaft sleeve 75 on the inner frame 46, the position of the pickup 74 relative to the inner frame 46 is set to the desired pivoting and optionally Verschiebungsfreiheitsgrad. The output shaft sleeve 75 thus serves to support the output shaft 30.

The spur gear drive gear 68 is engaged with not shown teeth of the crown gear 70 for simplicity reasons and forms due to the smaller number of teeth of the drive gear 68 relative to the crown gear 70 a reduction 76. The reduction 76 is a first gear stage of the transmission 48 in the form of a crown gear , The reduction ratio is 0.2 to 0.9, preferably 0.4 to 0.6, ie, the speed of the crown gear 70 is reduced by said reduction ratio relative to the engine speed and the torque increases accordingly. In this case, the drive axle 60 of the drive gear 68 is at least approximately at right angles to the crown gear axle 78 mounted in the inner frame 46 (see FIG. 6). Of course it is also possible to realize other reduction ratios or reduction systems and possibly other gear stages than Reductions should be interpreted.

In the embodiment illustrated in FIG. 5, the drive axle 60 is positioned parallel to, but not coaxially with, the output shaft 30. In order to arrange the brush attachment 14 inclined relative to the base body 14, the drive axle 60 and the output shaft 30 must also enclose the same angle. For reasons of ergonomics, an angle of less than 20 °, preferably between 3 ° and 10 °, is preferred. In this embodiment variant shown in FIGS. 53 to 56, the inner frame 46 is modified relative to the variant shown in FIG. 5 so that the output shaft 30, the output shaft sleeve 75 and the pickup 74 are at an angle to the drive axis 60. The drive shaft 60 of the drive gear 68 is, as in the embodiment shown in Figure 6, also oriented approximately at right angles to the mounted in the inner frame 46 Kronenradachse 78.

If, alternatively, there is a need to align the drive shaft 60 coaxially with the output shaft 30, the cam 72 can be manufactured as a separate component from the crown gear 70. This allows the

Drive shaft 60 and the output shaft 30 are positioned with a corresponding storage on the same flight. For this purpose, the pickup 74 is for this purpose, for example, to be rotated by 180 ° about its longitudinal axis and provided with a corresponding recess through which the cam 72 arranged on the crown wheel 70 in a rotationally fixed manner engages with sufficient clearance. On the toothed side surface of the crown wheel 70 of the cam 72 is firmly formed or can be firmly connected as an additional part of the crown wheel 70. Consequently, a complete revolution of the crown wheel 70 by 360 ° also leads to a complete rotation of the cam 72. The cam 72 may be designed in various forms in shape and arrangement with respect to the crown wheel axis 70, as shown by way of example in FIGS. In its various embodiments, the cam 72 has in each case at least one cam wall 80, which extends substantially parallel to the crown wheel axis 78 and at right angles to the toothed side face of the crown wheel 70.

As shown in FIG. 6, the pickup 74 clampingly engages the cam 72 and slidingly scans the cam wall 80 of the cam 72 by means of two rounded scan edges 82 at a fixed distance from each other. Due to the fixed spacing of the scanning edges 82 and the cross-section of the cam 72 deviating from a circular shape or, if appropriate, its eccentric arrangement with respect to the crown wheel axis 78, the pickup 74, together with the rotationally connected output shaft 30, is reversibly pivoted about its longitudinal center line within an angular range of less than 360 ° , Due to the pivotal movement of the pickup 74 and the thus different spacing of the scanning edges 82 from the crown wheel 70, it may be advantageous to slightly camber or shape the cam 72 in the direction of the crown wheel axis 78. Thereby, the pivotal movement of the pickup 74 and a reduction of the projected to a plane parallel to the toothed side surface of the crown wheel 70 distance between the Scanned edges 82 balanced. In a pivoting movement with small deflections of this circumstance can be neglected.

The ratio of the distance between the longitudinal center axis of the output shaft 30 and the longitudinal center axis of the

Drive axis 60 in the region of the pickup 74 to the distance between the longitudinal center axis of the cam 72 driving crown gear axis 78 and the longitudinal center axis of the crown gear 70 arranged cam 72 (ie the eccentricity of the cam 72) is at least 10: 1.

Since the cleaning element 40 is either fixedly arranged on the brush attachment 14 and the brush attachment 14 is attached directly to the output shaft 30 in a rotationally fixed manner - as in the embodiment of the electric toothbrush 12 shown in FIG. 2 - or indirectly via an attachment axis with a deflection element to the output shaft 30 is connected - as in the embodiment of the electric toothbrush 12 shown in FIG. 4 - the reversing pivotal movement of the output shaft 30 is transmitted to the cleaning element 40.

The output shaft 30 itself has a nearly constant diameter over its entire length, which is between 2 mm and 6 mm, preferably between 2.5 mm and 4 mm. On the brush side, the output shaft 30 is provided on both sides with flats 84 in its end. The flats 84 have the task, in cooperation with corresponding mating surfaces of the brush attachment 14 and the Aufsteckachse to transmit torque. Of course, it is also possible to equip the output shaft 30 with only one flat 84. The remaining cross section the output axis 30 is in the region of the flats 84 0.5 mm to 3.5 mm, preferably 1.5 mm to 2.5 mm. The length of the flats 84 along the output axis 30 is between 8 mm and 14 mm, preferably between 10 mm and 12 mm.

In the transition from the flattened cross section of the output shaft 30 to its full circular cross section almost flat shoulders 86 are formed. The shoulders form an angle with the longitudinal center line of the output shaft 30 from 30 ° to 60 °, preferably from 40 ° to 50 °. The beginning of the shoulders 86 is positioned about 15 mm to 22 mm, preferably 17.5 mm to 19.5 mm, measured from a face side 87 of the main body 10 (without connecting piece 32).

In the direction of the pickup 74, following the flats 84 on the output shaft 30, one, as shown in FIG. 5, or two, as shown in FIG. 6, are oppositely disposed notches 88. The notches 88 mediate the brush attachment 14 and the slip-on axis, respectively a stop in the axial direction and thus prevent unwanted removal or uncontrolled falling off of the brush attachment 14th

The notches 88 are disposed at a distance of about 12 mm to 20 mm, preferably 15 mm to 17 mm from the end face 87. They preferably have a depth of 0.2 mm to 0.8 mm, preferably from 0.35 mm to 0.65 mm. A bottom of the notches 88 has a width of about 0.3 mm to 1.5 mm, preferably 0.7 mm to 1.1 mm. The output shaft 30 is rounded brush head side in its end to reduce the risk of injury and to facilitate the assembly process when attaching the brush attachment 14.

The output shaft 30 is preferably made of a metal, such as stainless steel, and has a free length from the end face 87 measured from 25 mm to 35 mm, preferably from 28 mm to 32 mm.

In all brush heads 14, in which the neck 34 is moved, there is a free between the end face 87 and the neck-side end of the brush attachment 14

Distance to avoid contact and thus friction losses between the brush attachment 14 and the base body 10. This distance is between 0.2 mm and 0.8 mm, preferably between 0.4 mm and 0.6 mm.

Various embodiments of crown wheels 70 with cams 72 arranged thereon will now be described below with reference to FIGS. 8-11. In these figures, the teeth of the crown wheels 70 are not drawn for reasons of simplification and only symbolically represented by a ring. On the cam 72 opposite the toothed side surface of the crown gear 70 each cylindrical Kronach sleeves 90 are formed. They serve to support the crown wheel 70 along the crown gear axis 78 relative to the inner frame 46.

In Fig. 8, an embodiment of a cam 72 is shown. This cam 72 has a circular to slightly elliptical (with a ratio of Main vertex to side vertex of 1.01: 1 to 1.1: 1 preferably 1.03: 1 to 1.07: 1) cross-section and is eccentric with respect to the Kronenradhülse 90 and not shown Kronenradachse 78 arranged. The distance from the crown gear axis 78, which has the function of a rotation axis for the crown gear 70, to a center axis of the cam 72 is 0.5 mm to 3.0 mm, preferably 1.5 mm to 2.5 mm.

FIGS. 9 to 11 show embodiments of the cam 72 according to the invention. The

Cross-sections of the cams 72 each have an all-rounded shape of an n-corner, where n is an odd positive number. Thus, in FIGS. 9 and 10, cams with a substantially triangular cross-section and in FIG. 11 a cam with a substantially pentagonal cross-section are shown.

The cam walls 80 of the cams 72 are always rounded and also include the corners of the respective n-corner shape to allow a sliding scan through the sensing edges 82 of the pickup 74. The radius of curvature for the corners is 1.32 mm for the triangular section and 0.5 mm for the pentagonal section. The radius of the rounding of the sides is 7.27 mm in the triangular section and 14.44 mm in the pentagonal section. In general, the rounding radius for the corners decreases as n increases, ie approaches 0 mm, and the radius for rounding the sides increases as n increases. The cross-sectional shapes of the cam 72 must be designed according to each other due to the fixed distance of the scanning edges 82 and in particular have a radius. Preferably, the cross sections of the cams are designed as a rounded regular n-corner. The cam walls 80 of the cams 72 are each formed such that each bounded by the curve walls 80, in a cross-sectional plane of the cam 72 through the center of its cross-sectional shape extending cross-sectional length has approximately the same length.

The substantially n-corner cams 72 may be arranged eccentrically with respect to the crown gear axis 78 as well as concentrically with respect to the crown gear axis 78 as shown in FIGS. 10 and 11. For an octagonal cross-sectional shape of the cam 72, a complete reversal of the crown wheel 70 by 360 ° results in a n-fold reversing pivoting of the pickup 78 and the associated output shaft 30.

In an eccentric arrangement of an n-shaped cam 72 is a "large" reversing pivoting of

Customer of additional n "smaller" Verschwenkungen superimposed. Due to the eccentric arrangement of the

Cam 72 may be e.g. a dominant Grundverschwenkung be superimposed with a "large" swivel range of several "smaller" pivoting movements. In this case, the output shaft 30 pivots exactly once per revolution of the

Crown wheel 70 due to the eccentric arrangement of the

Cam 72 and n times due to the n-corner configuration of the cam 72. This arrangement will be described in detail below in connection with FIG. For n> 1, ie for cams 72 with 3, 5, 7... -Shaped cross-sectional shapes, the combination of the cam 72 with the pickup 74 forms an output-side second gear stage in the form of a gear-less gear ratio 92 (see, for example, FIG. 6). The corresponding transmission ratios 3, 5, 7 ... cause an increase in the pivoting frequency of the pickup 74 relative to the rotational speed of the crown wheel 70 by just these said ratios. The deflection of the pickup 74 causes a total (or total) depending on the specific cross-sectional shape of the cam 72, a maximum deflection of the pickup 74 and the associated output shaft 30 between 1 ° and 23 °, preferably between 3 ° and 15 °, especially preferably about 5 ° to 12 ° between its maximum deflection positions (ie the full deflection angle in a movement from the very left outside to the far right outside). Of course, it is also possible to set other ratios or additional ratios 92 or 70 before, in parallel or downstream.

The second gear stage is preferably housed in the main body 10 of the electric toothbrush 12. Of course, it would also be conceivable that at least one of the two gear stages is arranged in the brush attachment 14.

Of course, this particular embodiment by means of cam 72 and pickup 74 is only an example and other means not shown here can be used to implement the at least second, translating gear stage. Preferably, however, this second gear is not by means of toothing, but by means Realized curves or cams and correspondingly shaped customers.

The reversing pivoting movements respectively caused by the specific embodiments of cams 72 on the output shaft 30 will be described in detail below in connection with FIGS. 16 to 19. In FIG. 12, similar to the representation in FIG. 6, a structural unit consisting of the crown wheel, the cam 72, the pickup 74 and the associated output shaft 30 is shown. In contrast to the previously described embodiments, however, in this case the Kronach sleeve 90 shown in FIGS. 8 to 11 is replaced by a cam extension 94. This cam extension 94 passes through a Abtastausnehmung 96 in the pickup 74. The Abtastausnehmung 96 has a limited by a scan wall 98 rounded cross-section, within which the cam extension 94 can perform as low-friction rotation about the Kronenradachse 78 and at the same time a pivoting movement of the pickup 74 about the output axis 30 is enabled.

The cam extension 94 in the embodiment shown in Figs. 12 and 13 has a circular to slightly elliptical cross section (having a peak to peak ratio of 1.01: 1 to 1.08: 1, preferably 1.02: 1 to 1.05: 1) arranged eccentrically with respect to the crown wheel axis 78. The distance from the crown gear axis 78, which has the function of a rotation axis, to a center axis of the cam extension 94 is 0.1 mm to 1.5 mm, preferably 0.2 mm to 0.8 mm. As a result, in one revolution of the crown wheel 70, the pickup 74 is not only about the output shaft 30th pivoted, but due to the engagement of the cam extension 94 in the Abtastausnehmung 96 at the same time in the direction of the output shaft 30 reversibly translationally reciprocated back and forth. A detailed description of the mode of motion will be made in connection with FIG. 20.

In FIG. 13, the arrangement shown in FIG. 12 is again shown in a side view, wherein in particular the passage of the cam extension 94 through the scanning recess 96 can be clearly seen. The crown wheel 70 used in this arrangement with a concentrically arranged, substantially triangularly rounded cam 72 and a cam extension 94 placed above the cam 72, which has a substantially oval cross-section and is arranged eccentrically with respect to the crown wheel axis 78, is shown again in FIG. 14 shown exempted and enlarged.

All in terms of the cam 72 mentioned features in terms of its cross-sectional shape and the arrangement relative to Kronenradachse 78 can also on the

Cam extension 94 are transmitted. Specifically, this means that the cam extension 94 may be provided with a rounded, substantially n-corner-shaped cross section, where n is an odd positive

Number is and for n> 1, the formation of a gear-free further translation 100 is effected. In particular, the cam extension 94 can be arranged both eccentrically, as well as concentrically or coaxially with respect to the crown gear axis 78. In addition, the

Cam extension 94 formed such that each of its outer wall is bounded on two sides, in a cross-sectional plane of the cam extension 94 through the center of its cross-sectional shape extending cross-sectional length is at least almost the same length.

An example of a cam extension 94 having a triangularly rounded cross-section that is eccentric with respect to the crown wheel axis 78 is shown in FIG. The cam extension 94 is combined with a pentagon-shaped rounded cam 72 on the crown wheel 70. The cam 72 is here arranged concentrically or coaxially with respect to the crown wheel axis 78. A movement pattern that can be generated thereby on the output axis 30 will be explained below in connection with FIG. 20.

It should be noted at this point that it is of course also possible to form the embodiments of cams 72 shown in FIGS. 14 and 15 cylindrically and to arrange them concentrically with respect to the crown wheel 70. In this case, the output shaft 30 is merely reversibly translationally reciprocated and not additionally reversibly pivoted. The cylindrically shaped, concentrically arranged cam 72 stabilizes the pickup 74 laterally and prevents the pivoting movement. In the opposite case, if only a reversing pivotal movement is realized, the cam extension 94 is formed cylindrically and concentrically and stabilizes the pickup 74 in the direction of the output shaft 30 and prevents the translational movement. The caused by the rotation of the cam extension 94 reversing translational reciprocating motion causes the output shaft 30, a shift in its longitudinal direction between 0.5 mm and 2 mm, preferably between 0.5 mm and 1.5 mm. A reversing translational movement component of the cleaning element 40 can be realized, for example, in the embodiment of an inventive electric toothbrush 12 shown in FIG. It should be noted, however, that in this case appropriate safety measures must be taken so that no parts of the body or skin areas of the user can be trapped by the brush body 14, which lifts off from the base body 10. Such a safety measure is, for example, the insertion of a bellows-type hose between the end portion of the Aufsteckabschnitts 22 of the body 10 and the free end portion of the neck 34 of the brush attachment 14 or similar means of soft elastic material, which minimize the resulting gap by the translational movement of the brush attachment 14. Another safety measure is to let the brush attachment 14 end within the body 10 and thus to ban the risk of entrapment.

The movement patterns are explained with reference to the figures 16 to 20, which with the units shown on the left side, consisting of the

Crown gear 70, the cam 72, the Kronach sleeve 90 and the cam extension 94, can be achieved. In the graphs of FIGS. 16 to 19, the ordinate in each case represents a deflection angle φ during the pivoting of the output axis 30. In the case of a reversing translatory movement of the output axis 30, which can be done, for example, by a position reversal of the respective cam 72 shown with the associated Kronach sleeve 90, the ordinate also represents a deflection length s. In each case the time t or the corresponding rotational angle θ of the crown wheel 70 (or the drive axle 60) is plotted on the abscissa. The deflection angle φ is shown in each case for one complete revolution (rotational angle θ = 0..2π or 0..360 ⁰ ) of the crown wheel 70.

When ^'using a cam 72 with an oval cross-section which is mounted eccentrically with respect to the wheel shaft 78, there is a sinusoidal function of the

Deflection angle φ in the rotation of the crown wheel 70th

(Fig. 16). In this particular case, no translation 92 is realized by the second gear stage, but only a deflection in a reversing pivotal movement of the output shaft 30. The exact starting point of the curve depends on the position of the crown gear 70 relative to the pickup 74, the waveform itself, however equal.

When using a cam 72 with a substantially triangularly rounded cross-section and a centric arrangement with respect to the crown wheel axis 78 results in a transmission ratio of 3, which in the graph of Fig. 17 by a sinusoidal function with three deflection periods within a revolution of the crown wheel 70 for Expression comes. In addition, if the cam 72 were eccentric with respect to the crown wheel axis 78, then these three consecutive periods of oscillation would also be due to a sinusoidal displacement of one period within the rotation of the crown wheel 70, as shown for example in Fig. 16 modulated. The phase relationship between the two sinusoidal components depends on the exact position of the corners of the cam 72 to Kronenradachse 78 (see also Fig. 19).

18, the deflection angle φ of the output shaft 30 is shown as a function of the rotational angle θ of the crown wheel 70 or the time for a substantially pentagonal cam 72 arranged concentrically with respect to the crown wheel axis 78. In this case, the deflection angle φ passes through five sinusoidal periods in one revolution of the crown wheel 70. Consequently, there is a transmission ratio of 5.

FIG. 19 shows a movement pattern for the case of a substantially triangular cam 72 already mentioned in connection with FIG. 17, which is mounted eccentrically with respect to the crown wheel axis 78. In this case, the cam 72 is displaced along an angle bisector, from the center of the circumference of the cam cross section in the direction of a corner. Consequently, the functional dependence of the deflection angle φ on the rotational angle θ of the crown wheel 70 (or the drive axis 60) essentially results from a superimposition of the functional dependencies illustrated in FIGS. 16 and 17. Such a function curve leads to a jitter-like deflection of the output shaft 30. By a suitable choice of the number n of corners of the cam cross-section and a specific position of the cam 72 with respect to the crown wheel axis 78, a multiplicity can be achieved of displacement patterns by superimposing two sinusoidal oscillations.

In FIG. 20, the movement pattern of the output shaft 30 is shown under an additional influence of the cam extension 94. It is, as in the previous ones

Movement diagrams, on the ordinate of

Deflection angle φ of the output shaft 30 is applied. The

The abscissa in this case represents one

Displacement length s of the output axis 30. Also in this case, the movement pattern for a complete

Rotation of the crown wheel 70 by a rotation angle of 2π

(360 °).

Similar to the illustration in FIG. 17, the reversely pivoting movement component causes a sinusoidal variation of the deflection angle φ for three periods within one crown wheel revolution. At the same time causes the cam extension 94 with a cross-sectional geometry and arrangement as the cam 72 shown in FIG. 16, a reversing translational reciprocating motion along the output axis 30. Due to the frequency relationships, an operating point in this diagram initially goes through 1.5 deflection periods in a forward movement of the deflection angle φ and on the return movement in mirror image with respect to the abscissa the remaining 1.5 periods. In the selected representation of FIG. 20, a closed curve thus results with three almost elliptical curve elements. Also in this case, a variety of movement patterns by varying the cross sections of the cam 72 and the cam extension 94 and the choice of different positions of the cam 72 and the Cam extension 74 with respect to the Kronenradachse 78 can be achieved.

In the following table, for example, some forms of movement depending on the position and cross-sectional shape of the cam 72 and the cam extension 74 are listed.

In the above table, the remark "simple" means that exactly one complete swing period for the deflection angle φ is traversed per complete revolution of the crown gear 70. As previously mentioned, the variable n is to be replaced by an odd positive number, for example 3, 5, 7, 9 and so on. From the above table it can be seen that a large number of pivoting movements as well as reciprocating movements can lead to complex movement patterns of the output shaft 30 and the cleaning elements 40 connected thereto. These can be adapted to provide optimal cleaning of the teeth and dental interstices, as well as improved circulation of the gums by means of appropriate massage movements. Intensive tests with cleaning robots have shown that high-frequency movements with smaller deflections achieve the best cleaning values, especially in the interdental area. In particular, above-described overlapping movement patterns have proven to be useful. In particular, it has been possible to perfect the movement patterns of the so-called bass method, which is used for manual toothbrushes, with the method described above.

The pivoting movement of the movable cleaning element 40 is at a frequency between 3000 U / min and 15000 U / min, preferably from 8000 U / min to 12000 U / min, more preferably between 8'000 and 10'000 U / min. realized. The translational reciprocation of the cleaning element 40 is at a frequency between 1000 rpm and 12000 rpm, preferably between 2000 rpm and 4000 rpm or between 8000 rpm and 12000 rpm.

All of the movements of the output shaft 30 described above can in particular be transferred to the brush heads 14 in FIGS. 21-25 and 27-31. The brush attachment 14 shown in FIG. 26 is suitable, above all, for reversely pivoting movements of the output shaft 30 without interference with a translational reciprocating movement of the output shaft 30.

For all described embodiments of gears 48 it should be noted that the play between the teeth of the drive gear 68 and the crown gear 70 and between the cam 72 and the scanning edge 82 and the cam extension 94 and the Abtastwänden 98 is kept as low as possible to beat in the system and To keep a noise nuisance outside the body 10 as low as possible. In addition, the intermeshing elements may be provided with a lubricant, such as silicone grease, to reduce potential frictional effects. It is likewise possible to equip the components of the transmission 48, which are generally made of a hard material, completely or at certain contact or bearing points with a damping plastic in order to achieve the most uniform and low-noise conversion of the movements. In addition, for example, the output shaft 30 and the drive shaft 60 may be designed in several parts, wherein the individual part are connected to each other via coupling elements of a damping plastic. Due to this allowed torsional movements of the axes is a softer Start of the movements possible and a risk of injury from abrupt movements is reduced. Such a "soft bearing" can also be designed without interrupting the output shaft 30, for example by making the connection between the pickup 74 and the output shaft 30 soft, that is to say applying a soft layer between the two elements 74, 30. For noise reduction Also be designed corresponding bearings that dampen the vibration transmission via the output shaft 30.

Likewise, it is possible, for example, to coat the scanning edges 82 or the scanning walls 98 with a soft-elastic layer or to produce the entire pick-up 74 from a somewhat softer material. Furthermore, existing hollow or resonance chambers can be filled with sound-absorbing material for noise reduction in the interior of the body.

In the following, various embodiments of brush heads 14 and configurations of heads 38 and cleaning elements 40 and the bristles 42 arranged on them will be described in detail with reference to the further figures. These cleaning elements 40 are particularly suitable in connection with the movement patterns described above and enhance their effect.

In Fig. 21, a hard material made of

Brush head body 102 of a brush attachment 14, for example, on the main body shown in Fig. 1

10 is plugged and a reversing pivoting

Movement can be shown. The brush body 102 is preferably by means of produced by injection molding. It gives the brush attachment 14 a basic stability and serves as its backbone. In the neck-side end region of the brush head body 102, an opening 104 of an axle receptacle 106 is visible, in which the flattened end region of the output shaft 30 can be inserted. The axle receptacle 106 is equipped with two not visible in the illustrations Aufnahmeabflachungen, which are formed according to the flats 84 of the output shaft 30, and the interaction of which ensures the transmission of torque from the output shaft 30 to the brush attachment 14.

It can also be seen in this figure that the opening 104 is preceded by a cylindrical holding recess 107 on the end region side. The holding recess 107 serves to allow the brush attachment 14 to be placed on a corresponding holder for storage in a base station. The retaining recess 107 occupies a substantial part of the shark cross section and has a longitudinal depth of less than 10 mm, preferably less than 5 mm. The axle receptacle 106 and the retaining recess 107 are preferably arranged coaxially with one another. The retaining recess 107 can still cover a second function: by a corresponding configuration, a pivotable brush attachment 14 can be formed, which can also be plugged onto the main body 10 shown in FIGS. 3 and 4. In this case, an outer shell of the brush head 14 surrounding the retaining recess 107 surrounds the connecting piece 32 in an apron-like manner. The base body 10, which can be used both with brush heads 14 for oscillating movements and also for pivoting movements, are preferably only one Gear 48 equipped to provide the pivoting movement. An additional superimposed translational motion component appears less useful here.

On Aufsteckbürstengrundkörper 102 also supporting stumps 108 are formed from hard material both at the head end portion as well as in the neck-side portion. These Abstützstümpfe 108 serve various functions: the support in an injection mold in a subsequent injection molding process step for molding a soft elastic material, the support of the brush body 102 during labeling and optionally provide with their visible on the surface of the brush attachment surface 14 suitable areas on which labels, for example can be applied by hot stamping, inkjet or tampon Beschriftungsverfahren.

The brush head body 102 is already equipped with bristle receiving holes 110 on the head side. In addition, both on the top shown in Fig. 21 as well as the underside 44 shown in FIG. 22 each have a vent hole 112. The formed on the top 24 and the receiving side of the bottom 44 vent hole 112 is used in the injection molding of the support of a core Shaping the Achsaufnahme 106. The top vent opening 112 in the brush body 102 is covered in the subsequent injection molding process step of soft elastic material. The remaining under-side vent hole 112 is not covered with soft elastic material and serves to escape air during insertion of the Output shaft 30 and the flushing of the axle 106 with liquid for cleaning purposes.

In Fig. 22 is in the neck-side end of the

Brush body 102, between the two lower-side Abstützstümpfen 108, a substantially

U-shaped recess 113 visible. The U-shaped

Recess 113 surrounds a tongue-like spring element 114 with snap cam formed thereon, which has a notch

88 cooperates on the output shaft 30 to the brush attachment 14 on the main body 10 of the electric toothbrush

12 to hold.

FIGS. 23 and 24 show the upper side 24 and the lower side 44 of the brush-on brush body 102 shown in FIGS. 21 and 22, respectively, after overmolding with a flexible material. The over-molded with soft elastic material

Brush body 102 is then equipped with bristles 42 in the head region, for example, by means of a classic bristle method. The brush attachment 14 is preferably made of a plurality of plastic materials. Preferably, in each case a hard and a soft material is used. The different plastics adhere to each other. With a combined use of hard and soft materials in the brush attachment 14, a certain flexibility of the brush attachment 14 can be achieved. A combination of different layer thicknesses and shapes makes it easy to adjust the flexibility. Furthermore, with the soft material on the outer surface of the brush attachment 14, a structure can be formed, which is a removal of the brush attachment 14 from the main body 10th in which it provides a restrained structure for the fingers of the human hand.

To support the head 38 during injection molding of the soft elastic material and during the bristling process, a support surface 108 is mounted on the underside 44 of the brush head 38 which fixes and supports the brush head 38 during the bristling process.

The completed brush attachment 14 is shown in a sectional view in Fig. 25. In this

Sectional view is the one for the production of the

Brush body 102 used hard material shown with a different hatching than the soft-elastic material sprayed in a second process step. Particularly clear in this illustration, the axle 106 and the uncovered

Vent hole 112 visible.

Similarly, in Fig. 25, the spring element 114 clearly recognizable, which is formed on the brush attachment 14 on one side and therefore it allows the brush attachment 14 therefore to be plugged in two different orientations about its longitudinal axis on the base body 10. The spring element 114 is partially surrounded by soft elastic material. By varying the thickness of the hard material of the spring element 114, the extent of the snap-cam and a variation of the thickness of the surrounding soft elastic material, a trigger weight for removing the brush attachment 14 from the output shaft 30 can be precisely adjusted. The deduction weight is between 2 kg and 5 kg, preferably between 3.5 kg and 4.5 kg. The spring element 114 must already resiliently soften in the first injection molding process step, when removing the core, which serves to form the axle receptacle 106, due to its resilient properties. The same embodiment of the spring element 114 can also be used in an oscillating brush, as shown in FIG. 26.

On the bottom 44, the brush attachment shown in Fig. 25 on the head 38 may be additionally equipped with a rubber-elastic cleaning structure, not shown, in the form of a tongue cleaner. For this purpose, scraper edges are preferably formed from the soft elastic material, which can remove plaque and contaminants from the tongue during a movement. Similar soft elastic material can be used to form in the bristle field soft elastic massage elements, preferably rubber-elastic cleaning blades or cleaning structures. The scraper edges of soft elastic material are preferably transversely to the direction of movement of the brush head. If, for example, the brush head performs a reversing pivoting movement, then the scraper edges are essentially aligned in the longitudinal direction of the brush attachment 14. For example, if the brush head performs a translational reciprocating movement in the axial direction, then the scraper edges are substantially aligned in the transverse direction to the longitudinal axis, ie substantially at right angles to the longitudinal axis of the brush attachment 14. The cleaning structures may also be formed of hard material, which of course they are not rubber-elastic. FIG. 26 is a sectional view of the embodiment of a brush attachment 14 already shown in FIG. 4. This embodiment of the brush attachment 14 permits a reversingly rotating or reversely oscillating movement of the cleaning element 40. In this illustration, the slip-on axis 116 that can be pushed onto the output shaft 30 is particularly important the deflecting 118 clearly visible. Likewise, the adjusting element 36, whose position determines the relative positioning of the Aufsteckachse 116 within the neck 34 and consequently determines the pivoting angle range of the cleaning element 40, recognizable. The cleaning element 40 in this embodiment has a disk-shaped bristle carrier 120 and has been provided with bristles 42 during manufacture in a conventional plastic anchor, AFT (Anker Free Tufting) or IMT (In MoId Tufting) process.

The bristle carrier 120 is fastened on a turntable 122, which is mounted pivotably on the brush head body 102 via a turntable axis 124 which is fastened centrally in the turntable 122. The turntable axis 124 extends essentially at right angles to the longitudinal extent of the plug-on axis 116 or the output axis 30. The turntable 122 has a slot 126 into which the deflection element 118 engages. By changing the position of the Aufsteckachse 116 within the neck 34, which can be done via the control element 36, as already mentioned, the radial engagement position of the deflecting element in the turntable 122 is influenced, so that between a larger and smaller pivot angle of the turntable 122 and thus the Cleaning element 40 can be selected. The pivot angle is less than 35 °, preferably less than 30 °. Further information on the internal structure of this embodiment of a brush attachment 14 can be taken from CH 688537, for example.

Another embodiment of a brush attachment 14 with a pivotable cleaning element 40 is shown in FIGS. 27 and 28. In contrast to the embodiment shown in FIG. 2 and FIGS. 21 to 25, in which the entire brush attachment 14 is pivoted together with the cleaning element 40, the brush body 102 is attached firmly to the base 10, similar to the embodiment shown in FIG and not swiveling. The cleaning element 40 is fixedly connected to an axle extension 128. The axle extension 128 in turn is pivotally mounted in the brush body 102. When attaching this brush attachment 14 to the base body 10, similar to the case of the Aufsteckachse 116 (see FIG. 26), the Achsverlängerung 128 is connected to the output shaft 30. Due to flats 84, which cooperate with corresponding receiving sides of the axle extension 128, a torque is transmitted from the output shaft 30 to the axle extension 128. Seen from the outside, only the movable cleaning element 40 moves. In an alternative variant, the cleaning element 40 can also be arranged at an angle or inclined to the attachment axis 116. For reasons of ergonomics, the angle of inclination is preferably less than 30 °, particularly preferably less than 15 °. Thus, depending on the radial distance of the bristles 42 of the movable cleaning element 40 of the Aufsteckachse 116 42 different lengths are covered by the free ends of the bristles.

FIGS. 29 and 30 show a further development of the embodiment of a brush attachment 14 shown in FIGS. 27 and 28. In this case, alternately stationary cleaning elements 40s and pivotally movable cleaning elements 40 are arranged along the longitudinal extent of the brush attachment 14. The movable cleaning elements 40, as visible in Fig. 30, rotatably connected to the axle extension 128. When plug-on brush 14 is plugged onto base body 10 and the operating state of electric toothbrush 12 is activated, movable cleaning elements 40 pivot relative to stationary cleaning elements 40s, so that bristles 42 fastened to them also perform relative pivoting movements relative to one another. In this way, a particularly preferred cleaning effect is achieved. It should be noted that if the plug-on axle 116 or the axle extension 128 has to be carried out below the bristle field, the head 38 has to be made strongly thickened in order nevertheless to achieve the required stability. With a sufficient distance between the stationary and movable cleaning elements 40s and 40, the reversing pivoting movement, as already described, can be additionally superposed with a translational reciprocating movement.

Another embodiment of a brush attachment 14 is shown in FIGS. 31 and 32. Also in this embodiment, a pivotable cleaning element

40, which end-range side of the brush attachment 14th is arranged to be pivoted against a neck side positioned stationary cleaning element 40s. The pivotally movable cleaning element 40 is in turn rotatably connected to the axle extension 128 and is deflected in the active operating state of the electric toothbrush 12 due to a mechanical coupling with the output shaft 30 relative to the neck 34 and the stationary cleaning element 40s. In addition, this embodiment of a brush attachment 14 is also suitable for use in a combined movement with a reversing pivoting and a reversing translational motion component. The reversing translational movement component in this case causes a reciprocating movement of the pivotally movable cleaning element 40 along the longitudinal extent of the output shaft 30. For this purpose, the transmission 48, for example, those shown in Fig. 12 to Fig. 15 and in Fig. 20 Cam extension 94 on. The axle extension 128 can be made flexible in the area between the stationary and movable cleaning element 40s and 40 by a specific choice of material and / or a targeted material weakening. In this way, the movable cleaning element 40 can be deflected flexibly with respect to the stationary cleaning element 40s if the cleaning pressure is too high.

The embodiments of the brush attachment 14 illustrated in FIGS. 27 to 32 are each configured such that the neck 34 is connected such that it can be attached or detachably fixed to the connecting piece 32 and thus does not move with the movable cleaning elements 40. Preferably, the zones where the Aufsteckachse 116 from the Aufsteckbürstengrundkörper 102nd emerges at least partially surrounded by soft elastic material. This in turn serves as anti-trap protection and / or for sealing and storage. To compensate for the distances between stationary and movable cleaning elements 40s, 40, zones of specially designed soft material can be used in all design variants. These form a resilient buffer, which prevent pinching of lips, mouth surfaces, etc. For example, a concertina-type bellows could be formed of soft material. There are also other flexible, the movement compensating structures of soft material conceivable.

As an alternative to the arrangement of the cleaning elements 40, 40s shown in FIGS. 31 and 32, it is, of course, also possible to arrange stationary cleaning elements 40s in the free end region of the brush attachment 14 and to position the movable cleaning element 40 on the neck side. In addition, it is also conceivable to provide by means of two mutually parallel axle extensions 128 two pivotally movable cleaning elements 40 with different maximum deflection angles or a pivotally movable cleaning element 40 with two different maximum deflection angles. In this way, at least one pivotally movable cleaning element 40 can achieve a greater cleaning performance due to a larger maximum deflection angle.

Generally, for all described embodiments, the brush attachment 14 is considered to have a length of 55 mm to 85 mm, preferably 65 mm to 75 mm, measured from its free end to the shank end of the Brush head 14. The vent hole 112 opened in the completed brush head 14 is located in the longitudinal direction at a distance of 25 mm to 35 mm, preferably from 28 mm to 32 mm, from the shank-side end of the brush head 14. The snap-action cam of the spring element 114 in the embodiment shown in FIGS. 21 to 25 is located longitudinally between 12 mm to 20 mm, preferably 15 mm to 17 mm, away from the plug-on end of the brush attachment 14.

As the hard material for the above-described components, for example, polypropylene (PP), polyester (PET), polycyclohexanedimethanol terephthalate (PCT / PCT-A

(acid-modified) / PCT-G (glycol-modified)) polyethylene (PE), polystyrene (PS), styrene-acrylonitrile (SAN), polymethylmethacrylate (PMMA), acrylobutadiene-styrene

(ABS), polyoxymethylene (POM) or polyamide (PA) used.

Preferably, polypropylene (PP) with a

Young's modulus of 1000 N / m ² to 2400 N / m ² , preferably from 1300 N / m ² to 1800 N / m ² used.

As soft elastic material, for example, low density polyethylene (PE-LD), high density polyethylene (PE-HD), polyethylene (PE), polyvinyl chloride (PVC), elastomeric material such as polyurethane (PUR) or a thermoplastic elastomer (TPE), preferably a thermoplastic elastomer (TPE) used. Also possible is the use of polyolefin-based elastomer. The Shore A hardness of the soft elastic material used is preferably less than 90.

When using soft elastic material on the base body 10, for example for the adhesive elements 28, or in the formation of damping elements, in particular on the brush attachment 14, the thickness of layers of soft elastic material is more than 0.2 mm, preferably more than 0.5 mm. Soft elastic material with a Shore A hardness of less than 50, preferably less than 35, is used both on the main body 10, as well as on the brush attachment 14, for damping vibrations, vibrations and noise emissions that occur in the active operating state. These material properties provide a good compromise to optimally ensure the functions that are to be met with the soft elastic material. Optionally, thin layers of soft elastic material can also be formed in the erection section 18 or above labeling fields.

In addition, soft elastic material is also used for training for the head 38 and on the cleaning element 40 arranged cleaning elements, such as an already mentioned tongue cleaner or soft elastic cleaning blades. The soft-elastic cleaning blades can outside the bosten 42 standing around or arranged within bristle fields. The bristles 42 themselves are preferably made of polyamide or polyester with a diameter of 0.1 to 0.2 mm, preferably from 0.125 mm to 0.175 mm. They are arranged in bristle bundles. The relatively small-shaped head 38 has 20 to 30, preferably 22 to 28 bundles of bristles 42. Various forms of bristle arrangements are shown in the following FIGS. 33 to 41. The embodiments of cleaning elements 40 arranged on heads 38 shown in FIGS. 33 and 34 are particularly suitable for electric toothbrushes 12 which generate a reversingly pivoting or reversibly translational movement of the cleaning elements 40 in the active operating state. Analogous to the considerations with the tongue cleaner is preferably a part of the cleaning elements 40 aligned transversely to the direction of movement. In particular, this relates to elongated bristle bundles whose longitudinal extent in a plan view of the upper side 24 is greater than their transverse extent) or elongated, lamellar cleaning elements 40 made of soft material. In both embodiments shown, bristles 42 are combined into bundles of bristles above oblong rounded, sickle, C or crescent-shaped or oval bases. By aligning the elongated bristle bundles with their longitudinal axis at least almost parallel to the pivot axis of the cleaning elements 40, a wiping effect is achieved with a reversing pivoting movement. In particular, in the embodiment in Fig. 34 also bristle bundles are also arranged at right angles to the longitudinal axis of the neck 34 with its longitudinal axis in order to achieve such a wiping effect even with a reversing translational reciprocating movement of the head 38. The embodiment of a movable cleaning element 40 shown in FIG. 34 is therefore also particularly suitable for a combined movement of the cleaning element 40 with a reversingly pivoting and a reversing translational movement component. The illustrated embodiments of cleaning elements 40 can of course also be used in manual toothbrushes. With manual use become similar Cleaning movements, of course, with much lower frequency used.

The movable cleaning elements 40 shown in FIGS. 35 to 38 are arranged above a substantially circular or in the longitudinal direction slightly elliptically shaped bristle carrier 120 and in particular for use in reversing oscillating motion forms provided (see Fig. 4 and Fig. 26). In addition to circular bundles of bristles, these cleaning elements 40 with bristles 42 are also arranged above substantially elongate base surfaces (see FIGS. 35, 36) or else crescent-shaped base surfaces (see FIGS. 37 and 38). Also in this case, the longitudinal axes of the elongated base surfaces of the bristle bundles are preferably arranged at least approximately at right angles to the pivot axis about which the cleaning element 40 oscillates in a reversing manner.

In FIGS. 39 to 41, embodiments of cleaning elements 40 are shown in which stationary cleaning elements 40s are combined with pivotally movable cleaning elements 40, respectively. For example, in FIG. 39, a centrally arranged, pivotally movable cleaning element 40 on a circular bristle carrier 120, both at the free end region and at the neck side of the head 38, is surrounded by stationary cleaning elements 40s. In the embodiment shown in FIG. 40, the reversibly oscillatable cleaning element 40 is adjacent to a stationary cleaning element 40s, which is arranged at the free end region of the head 38 and has a rounded-triangular base area. In Fig. 41 is arranged only on the neck side of the pivotally movable cleaning element 40, a stationary cleaning element 40s. Of course, movable cleaning elements 40 according to FIGS. 35 to 38 can also be combined with the cleaning elements 40, 40s shown in FIGS. 39-41.

The bristles of the illustrated embodiments of cleaning elements 40 can be done in various ways, for example by means of conventional anchor plates or as already mentioned by means of IMT or AFT method. In particular, in the latter two methods, it is possible to produce bristle bundles with crescent-shaped, C-shaped, S-shaped, 8-shaped, n-cornered, circular, oval, etc. bases, which are formed symmetrically or asymmetrically. These bristle bundles with comparatively large expansions of the bases in different directions combine the wiping effects for different directions of movement of the cleaning elements 40. The two bristles also allow greater freedom of design with respect to the appearance of the bristle field.

In addition to bristles 42 rising from the bristle carrier 120 substantially at right angles or bundles of bristles 42, it is also possible to form bristles 42 arranged X-shaped on a cleaning element 40, 40s. The X-shaped bristles 42 are then at an angle of 3 ° to 20 °, preferably 8 ° to 14 ° to each other. In addition, it is possible to arrange bristles 42 or bristle bundles with longer and / or sharpened bristles 42, in particular on the outer edges of the cleaning elements 40, 40s. These then serve in particular for improved cleaning of the interdental spaces between the teeth. In addition, it is also possible to combine the cleaning elements 40 with bristles 42 on substantially round or slightly oval bases to bristle bundles, which then serve in particular the cleaning of a gum line. A total of 120 cylindrical, as well as one-sided or two-sided sharpened bristles 42 can be used on the bristle carriers, in each case pure or combined or in combination with additional massage and cleaning blades or cleaning structures made of soft material. The use of pointed bristles 42 on electric toothbrushes has already been described and referenced in detail in WO 2004/093718. The described heads or cleaning elements and production methods can be combined directly with the electric toothbrush 12 according to the invention.

The described brush heads 14 are preferably designed to be interchangeable. But it is also possible one

To make electric toothbrush 12 with the inventive transmission 48 and the brush attachment 14 so that this

Elements are integrally formed and the

Brush head 14 is not replaceable. This is especially the case with cheap battery devices.

For the sake of completeness, it should also be mentioned that the cleaning elements 40, 40s shown by way of example can also be replaced by other cleaning or active elements. In oral hygiene, these are, for example, generally interdental attachments, such as spiral brushes, toothpicks, etc., polishing elements, soft-elastic elements (eg professional cups) or tongue cleaner attachments. Of course, the transmission 48 according to the invention can also be used in other areas of personal care (face massage, nail care, head massage, wet and dry shaving, etc.) with correspondingly designed effective sets.

FIG. 42 shows a section of the inner life of a further embodiment of an electric toothbrush 12 according to the invention. The detail corresponds approximately to the illustration shown in FIG. 5 in connection with a previously described embodiment. Similar parts are provided in Fig. 42 with the same reference numerals as in Fig. 5. In contrast to the embodiment shown in FIG. 5, in the embodiment in FIG. 42, the transmission 48 is equipped with only one single gear stage. This gear stage is formed by a cam 72 and another pickup 132. The cam 72 is non-rotatably mounted on the not visible in Fig. 42 drive shaft 60 of the electric motor 58. In contrast to the embodiment in FIG. 5, the transmission 48 has no drive gear 68 and no crown gear 70. Due to the reduced number of gear elements and thus missing gear transmission, the transmission 48 of this embodiment produces less noise during operation and is simpler and less expensive to manufacture. The energy consumption and the preferred movement patterns (including Bewegungsfreguenz, deflection and angle of rotation) can be adopted by the previously described embodiments substantially analog. Like the embodiment shown in FIG. 5, the embodiment shown in FIG. 42 also has a control unit 52 arranged laterally from the electric motor 58 for controlling the operating states of the electric motor 58 and an inner frame 46 for fixing the position of the further pickup 132 to the output shaft 30 with respect to the cam 72 on. In the axial direction, parallel to the longitudinal axis of the output shaft 30, the pickup 132 is thereby supported on the one hand by a head bearing 134 of the inner frame 46 and on the other hand to the electric motor 58 through a stabilizing axis in its position.

As can be seen from FIGS. 43 and 44, the output shaft 30 extends parallel to the drive axis 60 indicated in the figures as a dashed line. If, in contrast to the embodiments shown, a parallel axial offset between the axes 30 and 60 is not desired, this can be achieved a correspondingly shaped spur gear with at least two gears whose first gear is seated, for example, on the drive shaft 60 and in a second gear on which the cam 72 is mounted, engages compensated.

In the embodiment shown in FIG. 42, the drive shaft 60 is parallel but not coaxial with

Output shaft 30 is positioned. In order to arrange the brush head 14 relative to the base body 14 in at an angle, and the drive shaft 60 and the

Output shaft 30 include the same angle. For reasons of ergonomics, an angle of less than 20 °, preferably less than 10 °, is preferred. In this embodiment variant, the inner frame 46 is opposite to that in FIG. 42 modified variant shown so that the output shaft 30, the output shaft sleeve 75 and the pickup 74, 132 are at said angle to the drive shaft 60. An illustration of this variant is shown in FIGS. 53 to 56.

As previously described, the further pickup 132 is positioned or fixed along its longitudinal direction by a stabilizing axle 136. Alternatively, however, a so-called pickup extension can be formed which extends the further pickup 132 in the direction of the electric motor 58 and is supported thereon. This form of guidance of the further pickup 132 will be further described in connection with FIGS. 53 to 56.

In the illustration of FIG. 44, it is shown particularly clearly how a closed circumferential gripper grip 142 of the further gripper 132 engages around the cam 72 radially with slight play. The pickup handle 142 is radially inward, the outer wall of the cam 72 opposite, equipped with a sensing wall 144. If, in the active operating state of the electric motor 58, the cam 72 is set in rotation about the drive axis 60, the outer wall of the cam 72 slides along the scanning wall 144 of the pickup handle 142 and moves the other pickup 132 together with its output shaft 30 in a reversing pivoting manner about the latter , The play between the sensing wall 144 and the cam 72 and optionally the use of elastic materials prevents on the one hand a "beating" of the output shaft 30, and damage to the electric motor 58 under heavy loads during cleaning operation. It is also possible, the buyer Umgriff 142 also unilaterally open, so fork-like form to to give it a higher elasticity and thereby avoid the mentioned "beating". The friction of the cam 72 on the sensing wall 144 can be reduced by using suitable lubricants. Also, to reduce the friction, it is possible to form the cam 72 slightly cambered and to reduce the size of the sliding surface by an edge-like design of the sensing wall 144. The crowning is described in detail in connection with FIG. 49.

FIGS. 45 to 48 show various perspective views of the further pickup 132. As previously mentioned, the pickup body 142 and furthermore a pickup recess 148 are formed on a pickup body 146. Said elements 132, 146, 142 are preferably made of a hard plastic material in an injection molding process. The rotationally fixed to the pickup body 146 arranged output shaft 60 is preferably made of a metal, such as a stainless steel.

As shown in FIGS. 46 to 48, the receiving recess 148 is formed on the opposite side of the pickup body 146 opposite the pickup handle 142 for the previously mentioned forced guidance of the further pickup 132. In this Abnehmerausnehmung 148 engages firmly on the inner frame 46 in the direction of the further Abnehmers 132 projecting pin in the form of the stabilizing axis 136 with a game. The stabilization axis 136 can be seen in FIGS. 42 and 43. Of course, it is also possible to provide a corresponding recess on the inner frame 46 and to arrange the pin on the further pickup 132. In the embodiment shown in FIGS. 45a and 45b, the pick-off recess 148 is essentially cylindrical or oval and provided with an inner diameter which allows a reversing pivoting movement of the further pickup 132 about the longitudinal axis of the output shaft 30 and at the same time a displacement of the further pickup 132 prevented in the longitudinal direction. Because of this Abnehmerausnehmung 148 in cooperation with the stabilizing axis 136 of the aforementioned subscriber extension is superfluous and no longer needed.

In the embodiment shown in Figures 47 and 48, however, the Abnehmerausnehmung 148 is formed slot-like, so that in addition a cam-type positive guidance of the further Abnehmers 132 is effected in the longitudinal direction. If, in an active operating state of the electric motor 58, the further pickup 132 reversely pivots about the longitudinal axis of the output shaft 30, a reversing translational oscillating component of the pickup 132 in the longitudinal direction of the output shaft 30 is generated at the same time.

The maximum longitudinal displacement in the reversing translational reciprocating component of the output shaft 30 is determined by a pitch angle α formed between the longitudinal axis of the pickup recess 148 and a transverse axis extending at right angles to the longitudinal axis of the output shaft 30 and the maximum rotational angle θ of the output shaft 30. The pitch angle α is preferably set smaller than 45 °, more preferably between 10 ° and 30 °. The resulting maximum longitudinal displacement in the reversible translational reciprocating motion is less than 2 mm, preferably less than 1 mm. In the linear, slot-like configuration of the pickup recess 148 shown in FIGS. 47 and 48, a gear ratio between the reversing pivoting component and the reversing translational component of 1: 1 is achieved. The superposition of the reversingly pivoting and reversing translational motion component leads to a closed trajectory of the cleaning element 40 connected to the output shaft 30. Depending on the embodiment of the recess 148, different movement patterns can be generated. With regard to further possibilities of generating various patterns of movement, reference should again be made at this point to FIGS. 16 to 20 and the table in the text. The shape of the recess 148 is not limited to that shown in Fig. 47, but may also be S- or C-shaped or designed as another, not straight curve shape. For example, wave-shaped shapes are also conceivable, by means of which larger transmission ratios of pivoting to translational movement components can also be achieved.

Two embodiments of cams 72 are shown by way of example in FIGS. 49 and 50. The cam 72 shown in FIG. 49 is substantially cylindrical, with its longitudinal central axis parallel to the longitudinal center axis of the drive axle 60 (indicated by dashed lines). The cam 72 is thus arranged eccentrically with respect to the drive axle 60. The itself when using such formed cam 72 resulting relationship between the deflection angle φ of the output shaft 30 and the

The rotational angle θ of the drive shaft 60 (or the time t) during a complete revolution of 360 ° (2π) is shown in FIG. 51. This functional relationship corresponds to the course shown in FIG. 16 and effects a 1: 1 translation of the rotational movement of the drive axle 60 into the reversingly pivoting movement of the pickup 132 or the output shaft 30.

The deflection angle φ follows a sinusoidal course and assumes in terms of magnitude maximum values as a function of the eccentricity of the arrangement of the cam 72 with respect to the drive axis 60 and the diameter of the cam 72. The 1: 1 ratio is mainly used in connection with an electric motor 58 for the previously described high speeds.

The cam 72 has a cambered shape, that is, its outer surface is slightly outwardly curved and does not run parallel to the outer surface of the drive shaft 60. In other words, the diameter of the cam 72 changes along the longitudinal extent of the cam 72 and causes this particular shape , At its ends, the cam 72 has a diameter of 4.5 mm to 5.5 mm, preferably 4.9 mm to 5.1 mm, while in the median plane has a maximum diameter of 5 mm to 6 mm, preferably 5.2 mm to 5.4 mm. The cambered surface has a radius of curvature between 95 mm and 115 mm, preferably between 100 mm and 110 mm. The ratio of the radii of curvature in the end region of the cam 72 to one of these radii is diameter at the end to Diameter in center plane 1.01: 1 to 1.3: 1, preferably 1.02: 1 to 1.1: 1.

The crowning of the cam 72 causes the active

Operating state less friction between the cam 72 and its outer surface and the other

Customer 132 occurs. This is also one

Noise reduction connected. The crowning is for the

Functionality of the transmission 48 is not mandatory. It is shown by way of example in FIGS. 49a and 49b. The cam 72 shown in Fig. 50 is not provided with a crown.

The distance between the longitudinal center axis of the cam 72 and the longitudinal center axis of its axis of rotation acting as driving axle 60 is 0.1 mm to 0.6 mm, preferably between 0.2 mm and 0.45 mm. This distance is a measure of the eccentricity or imbalance of the cam 72, which causes the deflection of the further pickup 132 during its rotation. The distance between the longitudinal center axes of the drive axle 60 and the output shaft 30 is between 3 mm and 9 mm, preferably between 5 mm and 7 mm, particularly preferably about 6 mm.

The ratio of the distances of the longitudinal center axes on the one hand from the output axis 30 to the drive axis 60 in the area of the pickup 74, 132 and on the other hand from the drive axis 60 to the eccentrically arranged cam 72 is 5: 1 to 90: 1, preferably at least 10: 1, particularly preferably 11 : 1 to 35: 1. This results in a small maximum (or full) deflection angle φ _tota i of the output axis 30 between outermost deflection positions of approximately 1 ° to 23 °, preferably of approximately 3 ° to 15 °, more preferably from about 5 to 12. This small maximum deflection angle φtotai in turn causes a small deflection of the cleaning elements 40, which in conjunction with the high speed of the electric motor 58 ensures a particularly effective and gentle cleaning of the teeth and the gums.

When using a lower speed electric motor 58, the gear ratio may be increased, for example, with the cam 72 shown in FIGS. 50 and 52 to achieve a higher moving frequency of the movable cleaning member 40. This embodiment of the cam 72 is arranged centrally with respect to the drive axle 60. The cam 72 has a rounded, substantially triangular cross-sectional shape. It corresponds in shape and function to the cam 72 already shown in FIGS. 10 and 17, but in this embodiment it is fastened directly on the drive axle 60. As is shown in FIG. 52, the functional dependence of the deflection angle φ of the output shaft 30 on the rotational angle θ of the drive shaft 60 (or the time t) for a complete rotation of the drive shaft 60 of 360 ° (2π) is determined by means of this cam 72 a

Translation realized from 1 to 3, i. during one

Rotation of the drive shaft 60 three complete swing motion cycles of the output shaft 30 are performed.

FIGS. 53 to 56 show a further embodiment of a transmission 48 according to the invention, in which the drive axle 60 is arranged inclined with respect to the output shaft 30. The further customer 132 is along its longitudinal direction by an already mentioned Abnehmerfortsatz 150 and the head bearing 134th supported. The customer extension 150 is tapered towards its free end region. Characterized a Abnehmerfortsatzspitze 152 is formed, which rises almost pointwise on a the electric motor 58 associated or provided on the inside of the body 10 support surface 154. The customer extension tip 152 is preferably formed in continuation of the longitudinal center axis of the output shaft 30, so that in the active operating state of the electric motor 58 only a point rotation about a contact point of the customer extension tip 152 results on the support surface 154. By appropriate measures, for example the application of a lubricant or the choice of suitable materials for the customer extension tip 152 and the support surface 154, a friction occurring thereby can be reduced. In addition, it is also possible, by means of a positive guidance formed in conjunction with the inner frame 46 by means of the stabilization axis 136, to completely dispense with placing the customer extension tip 152 on the support surface 154. In FIGS. 53 to 56, the cam 72 is arranged rotationally fixed on a cam carrier 156.

The angle formed between the brush attachment 14 and the base 14 is the same that is trapped between the drive shaft 60 and the output shaft 30. For ergonomic reasons, this angle is less than 20 °, preferably less than 10 °. In this embodiment variant, the inner frame 46 is modified relative to the variant shown in FIG. 42, so that the output shaft 30, the output shaft sleeve 75 and the further pickup 132 are at said angle to the drive axis 60. Of course, the use of all cams 72 described in connection with a multi-stage transmission 48, as shown for example in FIGS. 8 to 20, is also possible for a single-stage transmission 48. In particular, these cams 72 may have cross sections in the form of rounded n-corners, where n is an odd positive number. All other features of the previously described embodiments of electric toothbrushes 12 according to the invention can also be transferred to the embodiment shown in FIGS. 42 to 56.

Claims

claims

1. A gear for an electric toothbrush (12) for transmitting and forming a rotational direction oriented in a rotational direction, which is provided by an electric motor (58) on a drive axle (60), in a movement of an output shaft (30) for driving a movable cleaning element ( 40) of the electric toothbrush (12), wherein the transmission (48) has a cam (72) operatively connected to the drive axle (60) and a corresponding pickup (74, 132) rotatably connected to the output shaft (30) characterized in that a ratio of the distance between the longitudinal center axis of the output shaft (30) and the longitudinal center axis of the drive axle (60) in the region of the pickup (74,132) to the distance between the longitudinal center axis of the cam (72) driving axis (60, 78) and The longitudinal center axis of the cam (72) is at least 10: 1.

2. Transmission according to claim 1, characterized in that the output shaft (30) in the active operating state of the electric toothbrush (12) performs at least one reversing movement.

3. Transmission according to claim 1 or 2, characterized in that the transmission (48) in multiple stages with at least one drive-side first gear stage and at least one output-side second

Gear stage is equipped and at least one

Reduction (76) and at least one translation (92, 100).

4. Transmission according to claim 3, characterized in that the translation (92, 100) forms the output-side second gear stage and as a gear-free gear stage, preferably as a cam gear is designed.

5. Transmission according to one of claims 1 to 4, characterized in that the cam (72) has a cross section in the form of a rounded, preferably regular n-corner, where n is an odd positive number, the n-corner has a radius and all corners and sides are rounded, or that the cam (72) has a substantially circular cross section and is mounted eccentrically with respect to its axis (60, 78) driving it.

6. Transmission according to claim 5 or 6, characterized in that a cam wall (80) of the cam (72) is formed such that each of the cam wall bounded on two sides, in a cross-sectional plane of the cam (72) through the center of its cross-sectional shape extending cross-sectional length at least nearly the same length.

7. Transmission according to one of claims 1 to 6, characterized in that the drive axle (60) is aligned inclined to the output shaft (30) and preferably enclose an angle between 3 ° and 10 °.

8. Electric toothbrush with a base body (10), which forms a handle (16) and receives an electric motor (58) and a transmission (48) according to one of claims 1 to 7, a to the main body (10) subsequent neck (34) and one on the neck (43), opposite the handle (16) arranged head

(38), which is equipped with a movable cleaning element (40), wherein the drive axis (60) of the

Electric motor (58) in the attached state with unloaded operation of the electric toothbrush (12) at a rotational speed between 2000 U / min and 12000 U / min, preferably between 3000 U / min and 8000 U / min.

9. Electric toothbrush according to claim 8, characterized in that the movable cleaning element (40) performs a reversing pivoting movement with a frequency between 3000 U / min and 15000 U / min, preferably between 8000 U / min and 12000 U / min.

10. Electric toothbrush according to claim 9, characterized in that the movable cleaning element

(40) in the pivoting movement in total by 1 ° to 23 °, preferably by 3 ° to 15 °, more preferably by about 5 ° to 12 ° between its two maximum deflection positions is deflected.

11. Electric toothbrush according to claim 9 or 10, characterized in that the pivoting movement of the movable cleaning element (40) is superimposed at least one further pivoting movement.

12. Electric toothbrush according to one of claims 9 to 11, characterized in that the movable cleaning element (40) on the head (38) of a brush attachment (14) is arranged and that the pivoting movement of the movable cleaning element (40) about an axis which at least almost parallel to the longitudinal axis of the neck (34), moves.

13. Electric toothbrush according to one of claims 9 to 11, characterized in that the movable cleaning element (40) on the head (38) of a brush attachment (14) is arranged and the pivoting movement about an axis which is at least approximately at right angles to the longitudinal axis of the neck (34 ) runs, performs.

14. Electric toothbrush according to one of claims 8 to 13, characterized in that the movement of the movable cleaning element (40) has a reversing translational reciprocating motion component whose direction of movement extends at least almost parallel to the longitudinal axis of the neck (34).

15, electric toothbrush according to claim 14, characterized in that the reversing translational reciprocating motion component of the movable cleaning element (40) is superimposed on at least one further reversing translational reciprocating motion component.

16. Electric toothbrush according to claim 14 or 15, characterized in that the reversing translational reciprocating motion component has a frequency between 1000 U / min and 12000 U / min, preferably between 8000 U / min and 12000 U / min.

17. Electric toothbrush according to one of claims 8 to 16, characterized in that the movable cleaning element (40) is provided with cross-sectionally elongated bundles of bristles (42) and / or elongated rubber-elastic cleaning blades or cleaning structures, which with their longitudinal axis are aligned transversely to the direction of movement of the cleaning element (40).

18. Electric toothbrush according to one of claims 8 to 17, characterized in that the head (38) additionally comprises a stationary cleaning element (40s) which is fixedly arranged with respect to the neck (34).

19. Electric toothbrush according to one of claims 8 to 18, characterized in that the transmission (48) formed in one stage and a cam (72) which is arranged rotationally fixed directly to the drive axle (60).

20. Electric toothbrush according to one of claims 8 to 19, characterized in that the electric toothbrush (12) has a preferably eccentrically mounted flywheel, which is operatively connected to a drive axle (60) of the electric motor (58).

21. Electric toothbrush according to one of claims 8 to 20, characterized in that the output shaft (30) by a cam-type positive guide is capable of performing in the active operating state of the electric motor (58) has a reversing translational reciprocating motion component.

22. Electric toothbrush according to claim 19, characterized in that a pick-up (74, 132) surrounds the cam (72) in a clip-like manner open or circumferentially closed.

23. gear for an electric toothbrush (12) for transmitting and forming a rotational direction oriented in a rotational direction, by an electric motor - IA -

(58) on a drive axle (60) is provided, in a movement of an output shaft (30) for driving a movable cleaning element (40) of the electric toothbrush (12), characterized in that the transmission (48) in multiple stages with at least one drive-side first gear stage and at least one output-side second gear stage is equipped and at least one reduction (76) and at least one translation (92, 100).

24. Electric toothbrush with a base body (10) which forms a handle (16) and receives an electric motor (58) and a gear (48), one of the base body (10) subsequent neck (34) and one on the neck (43) opposite to the handle (16) arranged head (38) on which a driven axis (30) connected, movable cleaning element (40) is arranged, wherein the transmission (48) has a cam (72) connected to a drive axis of the electric motor (58) is operatively connected, and a pickup (74, 132) which is rotatably connected to the output shaft (30), characterized in that the cam (72) has a cross section in the form of a rounded n-corner, where n an odd positive number.