Support structure

Abstract

The present invention provides a support structure for supporting a driving shaft that reciprocates. The support structure (20) includes an inner fixed ring (23) of the support structure, at least one elastic member (22) of the support structure, and an outer fixed ring (21, 51) of the support structure. The inner fixed ring (23) of the support structure is fastened to the driving shaft (10), the outer fixed ring (21) of the support structure is fastened to the inner wall of the lower housing of the device, and the elastic members (22) of the support structure are distributed between the outer fixed ring (21) and the inner fixed ring (23) of the support structure. The width (b1) in the direction perpendicular to the driving force (F1) of the cross-section of the elastic member (22) of the support structure perpendicular to the radial direction of the driving shaft (10) is greater than three times the thickness (t1) in the direction parallel to the driving force (F1) of the cross-section of the elastic member (22) of the support structure perpendicular to the radial direction of the driving shaft (10). The support structure has the advantages of low noise, low energy loss, low cost, simple structure, and being suitable for mass production.

Description

Technical Field

[0001] The present invention relates to a support structure, and more particularly to a support structure for supporting a drive shaft that reciprocates in an electric cleaning and care appliance. Background Art

[0002] Generally, a drive shaft that undergoes reciprocating motion (e.g., reciprocating rotational motion or reciprocating linear motion) needs to be supported by one or more support members to maintain its normal operation. In the prior art, an axle-hole fitting structure such as a bushing is commonly used to support the drive shaft, and there is a clearance fit between the drive shaft and the bushing hole. Such a support structure often has relatively high noise and energy loss. The drive shaft can also be supported by bearings. For example, a ball bearing can be used to support a drive shaft that undergoes reciprocating rotational motion, and a linear bearing can be used to support a drive shaft that undergoes reciprocating linear motion. However, the cost of using bearings for support is relatively high. Summary of the Invention

[0003] The object of the present invention is to provide a support structure for supporting a drive shaft that undergoes reciprocating motion, which has the advantages of low noise, low energy loss, and low cost, and is simple in structure and suitable for mass production.

[0004] To achieve the above object, in the present invention, at least a part of the drive shaft is included in the lower housing. Driven by a driving force, the drive shaft reciprocates relative to the lower housing of the device along / around its longitudinal axis. The lower housing of the device further includes a support structure for supporting the drive shaft. The stationary upper housing of the device includes a head driven by the drive shaft, and the transverse axis of the head is substantially perpendicular to the longitudinal axis of the drive shaft. Wherein, the support structure includes an inner fixing ring of the support structure, at least one elastic member of the support structure, and an outer fixing ring of the support structure. The inner fixing ring of the support structure is fastened to the drive shaft along the circumferential direction of the drive shaft. The outer fixing ring of the support structure is directly or indirectly fastened to the inner wall of the lower housing of the device. The elastic member of the support structure has the properties of a spring and is distributed between the outer fixing ring of the support structure and the inner fixing ring of the support structure. The outer end of the elastic member of the support structure is fixedly connected to the outer fixing ring of the support structure, and the inner end of the elastic member of the support structure is fixedly connected to the inner fixing ring of the support structure. Wherein, the dimension of the elastic member of the support structure along the direction perpendicular to the driving force is set as the width, and the dimension of the elastic member of the support structure along the direction parallel to the driving force is set as the thickness. The width of the elastic member of the support structure along the direction perpendicular to the driving force is more than three times its thickness along the direction parallel to the driving force, and the length of the elastic member of the support structure along the radial direction of the drive shaft is more than three times the thickness of the elastic member along the direction parallel to the driving force, so that the axial bending deformation section coefficient of the elastic member is less than one-ninth of the circumferential bending deformation section coefficient, or the circumferential bending deformation section coefficient of the elastic member is less than one-ninth of the axial bending deformation section coefficient, and the natural frequency of the elastic system formed by the elastic member and the movement frequency of the drive shaft are in the resonance range, resulting in a reduction in the energy loss between the elastic member and the drive shaft.

[0005] The outer fixing ring of the support structure, the elastic member of the support structure, and the inner fixing ring of the support structure can be made of plastic, preferably made of thermoplastic, and the inner fixing ring of the support structure and the drive shaft can be injection-molded into an integral part. The elastic member of the support structure can also be integrally connected to the inner and outer fixing rings of the support structure.

[0006] In one embodiment, the thickness of the elastic member of the support structure along the direction parallel to the driving force is 0.1 mm - 1.3 mm. In another embodiment, the thickness of the elastic member of the support structure along the direction parallel to the driving force is 0.2 mm - 0.7 mm.

[0007] The electric cleaning and care appliance of the present invention is preferably an electric toothbrush or a dental irrigator, and the support structure is a linear motion support structure for supporting a drive shaft that reciprocates linearly along a longitudinal axis. Preferably, the distance between the upper surfaces of the inner and outer fixing rings of the linear motion support structure and the head is less than the distance between the upper edge of the elastic member of the linear motion support structure and the head, or the distance between the lower surfaces of the inner and outer fixing rings of the linear motion support structure and the head is greater than the distance between the lower edge of the elastic member of the linear motion support structure and the head, so that at least one of the upper and lower sides of the cross-section parallel to the longitudinal axis of the drive shaft that reciprocates linearly of the combined linear motion support structure is concave in shape. Preferably, under the action of the reciprocating linear motion driving force, the maximum motion amplitude of the reciprocating linear motion drive shaft along its longitudinal axis is less than 3 mm, and more preferably, the maximum motion amplitude is 2 mm.

[0008] In another embodiment, the electric cleaning and care appliance is an electric toothbrush in which the drive shaft reciprocally rotates about its longitudinal axis, and the support structure is a rotary motion support structure for supporting the drive shaft that reciprocally rotates. Under the action of the reciprocating rotary driving force, the inner end of the elastic member of the rotary motion support structure reciprocally bends about the outer end of the elastic member of the rotary motion support structure. Preferably, the amplitude of the maximum rotation angle of the reciprocating rotary drive shaft about its longitudinal axis is less than 40 degrees, and more preferably, the maximum rotation angle amplitude is 25 degrees.

[0009] In the present invention, due to the reasonable selection of the numerical ratio between the thickness of the elastic member of the support structure along the direction parallel to the driving force and the width along the direction perpendicular to the driving force, for the drive shaft that reciprocates linearly, the elastic member of the support structure is not only easily bent and deformed in response to the reciprocating linear motion of the drive shaft along its longitudinal axis under the drive of the reciprocating linear motion driving force, but also can prevent the drive shaft from rotating about its longitudinal axis, and thus can reliably generate elastic bending deformation in response to the driving force of the drive shaft; for the drive shaft that reciprocates rotationally, under the drive of the reciprocating rotary motion driving force, the elastic member of the support structure is not only easily bent and deformed in response to the reciprocating rotary motion of the drive shaft about its longitudinal axis, but also can prevent the drive shaft from moving along its longitudinal axis, and thus can reliably generate elastic bending deformation in response to the driving force of the drive shaft. At the same time, because there is no clearance connection between the drive shaft and the support structure, the impact and collision on the support structure caused by the reciprocating motion of the drive shaft are avoided, the noise is greatly reduced, and in addition, the energy loss during the conversion between the elastic potential energy of the elastic member of the support structure and the driving kinetic energy of the drive shaft is very small, so it has the advantages of simple structure, low noise and small energy loss. Description of the Drawings

[0010] Figure 1Front view of the reciprocating linear motion combination of the drive shaft and its support structure for reciprocating linear motion of the present invention. The support structure shown in the figure includes a plurality of support structure elastic members;

[0011] Figure 2 For Figure 1 Front views of the reciprocating linear motion combination shown in different working states. Among them, Figure 2-1 Shows the situation where the reciprocating linear motion drive shaft is at the origin position (i.e., the middle position) of its linear motion trajectory. Some reciprocating linear motion support structure fixing members can be seen in the figure. Figure 2-2 Shows the situation where the reciprocating linear motion drive shaft is at the origin position of its linear motion trajectory. In the figure, the reciprocating linear motion support structure fixing members are completely disassembled. Figure 2-3 Shows the reciprocating linear motion drive shaft leaving Figure 2-2 The situation where it moves upward along its longitudinal axis from the origin position of the shown motion trajectory. Figure 2-4 Shows the reciprocating linear motion drive shaft leaving Figure 2-2 The situation where it moves downward along its longitudinal axis from the origin position of the shown motion trajectory. Figure 2-5 Shows the situation where there is one linear support structure elastic member. The reciprocating linear motion drive shaft shown in the figure is at the origin position of its linear motion trajectory.

[0012] Figures 3 to 3 -3 is a cross-sectional view of the reciprocating linear motion combination shown in Figures 2 to 2 -4 in corresponding working states. Among them, Figure 3-1 Corresponding to the working state shown in Figure 2-2 Shown, Figure 3-2 Corresponding to the working state shown in Figure 2-3 Shown, Figure 3-3 Corresponding to the working state shown in Figure 2-4 Shown;

[0013] Figure 4 Front view of the reciprocating rotary motion combination of the drive shaft and its support structure for reciprocating rotary motion of the present invention. The support structure shown in the figure includes a plurality of support structure elastic members;

[0014] Figure 5 For Figure 4 Front views of the reciprocating rotary motion combination shown in different working states. Among them, Figure 5-1 Shows the situation where the reciprocating rotary motion drive shaft installed with the reciprocating rotary motion support structure fixing members is at the origin position of its rotary motion trajectory. Figure 5-2 Shows the situation where the reciprocating rotary motion drive shaft is at the origin position of its rotary motion trajectory. In the figure, the reciprocating rotary motion support structure fixing members are completely disassembled. Figure 5-3 Shows the reciprocating rotary motion drive shaft leaving Figure 5-2The case where the origin position of the shown movement trajectory rotates in the clockwise direction, Figure 5-4 shows the reciprocating rotary motion drive shaft leaving Figure 5-2 The case where the origin position of the shown movement trajectory rotates in the counterclockwise direction;

[0015] Figure 6 is the bottom view of the reciprocating rotary motion combination shown in Figure 5 being in the corresponding working state, where, Figure 6-1 corresponding to Figure 5-1 the shown working state, Figure 6-2 corresponding to Figure 5-2 the shown working state, Figure 6-3 corresponding to Figure 5-3 the shown working state, Figure 6-4 corresponding to Figure 5-4 the shown working state;

[0016] Figures 7 to 7 -4 is the perspective view of the reciprocating rotary motion combination shown in Figures 5 to 5 -4 being in the corresponding working state, where, Figure 7-1 corresponding to Figure 5-1 the shown working state, Figure 7-2 corresponding to Figure 5-2 the shown working state, Figure 7-3 corresponding to Figure 5-3 the shown working state, Figure 7-4 corresponding to Figure 5-4 the shown working state, Figure 7-5 shows the case where the elastic member of the rotary support structure is one, and the reciprocating rotary motion drive shaft shown in the figure is at the origin position of its rotation motion trajectory;

[0017] Figure 8 is a schematic diagram of an electric toothbrush equipped with a linear motion combination as shown in Figure 1 ;

[0018] Figure 9 is a schematic diagram of an electric toothbrush equipped with a rotary motion combination as shown in Figure 4 ;

[0019] Figure 10 is a schematic diagram of a dental irrigator equipped with a linear motion combination as shown in Figure 1 ;

[0020] Description of Main Reference Numerals

[0021] 10 is the drive shaft, which performs reciprocating linear motion along the longitudinal axis of the drive shaft, hereinafter simply referred to as the translation shaft;

[0022] 20 is the linear motion support structure for supporting the reciprocating linear motion drive shaft, hereinafter simply referred to as the straight-support structure;

[0023] 21 is the outer fixing ring of the reciprocating linear motion support structure, hereinafter simply referred to as the straight-support structure outer fixing ring;

[0024] 22 is the elastic member of the reciprocating linear motion support structure, hereinafter simply referred to as the straight-support structure elastic member;

[0025] 23 is the inner fixing ring of the reciprocating linear motion support structure, hereinafter simply referred to as the straight-support structure inner fixing ring;

[0026] 30 is the fixing member of the reciprocating linear motion support structure, hereinafter simply referred to as the straight-support structure fixing member;

[0027] 40 is the drive shaft that performs reciprocating rotational motion around the longitudinal axis of the drive shaft, hereinafter simply referred to as the rotating shaft;

[0028] 50 is the rotational motion support structure that supports the reciprocating rotational motion drive shaft, hereinafter simply referred to as the rotation-support structure;

[0029] 51 is the outer fixing ring of the reciprocating rotational motion support structure, hereinafter simply referred to as the rotation-support structure outer fixing ring;

[0030] 52 is the elastic member of the reciprocating rotational motion support structure, hereinafter simply referred to as the rotation-support structure elastic member;

[0031] 53 is the inner fixing ring of the reciprocating rotational motion support structure, hereinafter simply referred to as the rotation-support structure inner fixing ring;

[0032] 60 is the fixing member of the reciprocating rotational motion support structure, hereinafter simply referred to as the rotation-support structure fixing member;

[0033] L 1 is the longitudinal axis of the reciprocating linear motion drive shaft;

[0034] h 1 is the length of the straight-support structure elastic member along the radial direction of the reciprocating linear motion drive shaft;

[0035] b 1 is the width of the straight-support structure elastic member along the direction perpendicular to the driving force F 1 The dimension in the direction is the width;

[0036] t 1 is the thickness of the straight-support structure elastic member along the direction parallel to the driving force F 1 The dimension in the direction is the thickness;

[0037] L 2 is the longitudinal axis of the reciprocating rotational motion drive shaft;

[0038] h 2is the length of the rotating-support structure elastic member in the radial direction of the reciprocating rotation motion driving shaft;

[0039] b 2 is the dimension of the rotating-support structure elastic member perpendicular to the driving force F 2 and is the width;

[0040] t 2 is the dimension of the rotating-support structure elastic member parallel to the driving force F 2 and is the thickness;

[0041] F 1 is the force that drives the driving shaft to perform a reciprocating linear motion along its longitudinal axis;

[0042] F 2 is the force that drives the driving shaft to perform a reciprocating rotational motion around its longitudinal axis. Detailed implementation manners

[0043] In the following description of the present application, terms expressing relative spatial positions such as "inner", "outer", "upper", "lower", "upper part (or upper end)", "lower part (or lower end)" are used to simply describe the mutual relationship between one element or feature and another element (one or more) or feature (one or more) as shown in the figure. In this specification, "inner" and "outer" are relative to the radial direction of the electric cleaning and care appliance, with the vicinity of its center defined as inner and away from the center defined as outer; "upper", "lower", "upper part", "lower part", "upper end", "lower end" are relative to the longitudinal axis of the electric toothbrush. When the electric cleaning and care appliance is in an upright or inclined working state, the vicinity of the bristle end is defined as "upper", "upper part", or "upper end", and the opposite end is defined as "lower", "lower part", or "lower end".

[0044] When an element is described as "on..." or "connected to" another element, it may be directly located on or connected to the other element, or there may be intervening elements. When an element is described as "directly on..." or "directly connected to" another element, there are no intervening elements there. Other words describing the relationship between elements should be understood to have similar meanings (for example, "between..." is opposite to "directly between...", etc.).

[0045] The stationary device housing (not shown in the figure) of the present invention includes an upper housing and a lower housing. The lower housing includes at least a part of the driving shaft 10 or 40 and a support structure 20 or 50 for supporting the driving shaft 10 or 40. Under the action of the driving force F 1 or F 2 the driving shaft 10 or 40 moves along its longitudinal axis L 1 or rotates around its longitudinal axis L 2Make a reciprocating linear motion or a reciprocating rotary motion relative to the lower housing of the device. The upper housing of the device includes a head driven by drive shafts 10 and 40, and the transverse axis L of the head 3 、L 4 is substantially perpendicular to the longitudinal axes L 1 、L 2 of the drive shafts 10 and 40. Figure 1-3 shows the case where the drive shaft 10 makes a reciprocating linear motion along its longitudinal axis L 1 ; Figure 4-7 shows the case where the drive shaft 40 makes a reciprocating rotary motion around its longitudinal axis L 2 .

[0046] Referring to Figure 1-7 , the support structures 20 and 50 of the present invention include inner fixing rings 23 and 53 of the support structure, at least one elastic member 22 and 52 of the support structure, and outer fixing rings 21 and 51 of the support structure. Among them, Figure 2-5 and Figure 7-5 show the case where there is one elastic member of the support structure, Figure 2-1 to Figure 2-4 and Figure 7-1 to Figure 7-4Shown is the case where there are multiple support structure elastic members. The outer fixing rings 21, 51 of the support structure, the support structure elastic members 22, 52, and the inner fixing rings 23, 53 of the support structure can be made of plastic, preferably made of thermoplastic. The inner fixing rings 23, 53 of the support structure are fastened to the drive shafts 10, 40 along the circumferences of the drive shafts. The inner fixing rings 23, 53 of the support structure move together with the reciprocating drive shafts 10, 40, and there is no relative movement between them. The inner fixing rings 23, 53 of the support structure and the drive shafts 10, 40 can be injection-molded together into an integral part, or they can be separate parts fastened together through fittings. The outer fixing rings 21, 51 of the support structure are fastened to the inner wall of the lower housing of the device along the circumference of the lower housing of the device directly or through the support structure fixing members 30, 60. There is no relative movement between the outer fixing rings 21, 51 of the support structure and the support structure fixing members 30, 60 (when fastened through the fixing members) and the lower housing of the device. That is to say, the support structure fixing members 30, 60 and the outer fixing rings 21, 51 of the support structure are all stationary relative to the lower housing of the device. At least one support structure elastic member 22, 52 is distributed between the outer fixing rings 21, 51 and the inner fixing rings 23, 53 of the support structure. However, the present invention is not limited thereto. The support structure elastic members 22, 52 of the present invention can be integrally connected to the inner and outer fixing rings 21, 51 and 23, 53 of the support structure 20, 50, such as in a circular ring shape, or some of the support structure elastic members can be connected to a part of the inner and outer fixing rings. These modifications do not exceed the scope of the present invention. In addition, the cross-section perpendicular to the radial direction of the drive shaft of the support structure elastic members 22, 52 of the present invention can be of any shape, such as a polygon or a combination of a straight line segment and an arc segment, etc. These modifications also do not exceed the scope of the present invention.

[0047] As Figure 2-2 to Figure 2-5 and Figure 6-2 to Figure 6-4 and Figure 7-5 shown, the ends of the support structure elastic members 22, 52 fixed to the outer fixing rings 21, 51 of the support structure are the outer ends A, C, and the other ends of the support structure elastic members 22, 52, which are opposite to the outer ends A, C and fixed to the inner fixing rings 23, 53 of the support structure, are the inner ends B, D. Of course, the lower housing of the device or the reciprocating drive shaft can also be of other shapes, and the inner and outer fixing rings of the support structure can also be shapes matching the lower housing of the device or the reciprocating drive shaft.

[0048] Figure 1-3 Shown is the case where the drive shaft 10 makes a reciprocating linear motion. Referring to Figure 2-2 , Figure 2-5 and Figure 3-1, when the translation axis 10 is at the origin position of its reciprocating linear motion trajectory (the middle position of the linear reciprocating motion trajectory), the straight-support structure 20 is also at the origin position. At this time, the straight-support structure elastic member 22 is in a free state, and the straight-support structure elastic member 22 does not produce elastic bending deformation. Refer to Figure 2-3 and Figure 3-2 , when the translation axis 10 leaves the origin position and moves upward along its longitudinal axis L 1 , since the inner fixing ring 23 in the straight-support structure is fastened to the translation axis 10, the translation axis 10 drives the inner fixing ring 23 in the straight-support structure to move upward. The inner fixing ring 23 in the straight-support structure then drives the inner end B of the straight-support structure elastic member 22 to move upward. The outer end A of the straight-support structure elastic member is fixedly connected to the outer fixing ring 21 of the straight-support structure, and the outer fixing ring 21 of the straight-support structure is stationary relative to the lower housing of the device. Therefore, the translation axis 10 produces relative motion with respect to the outer end A of the straight-support structure elastic member. The straight-support structure elastic member 22 undergoes elastic bending deformation under the action of the relative motion of the translation axis 10. More specifically, when the translation axis 10 drives the inner end B of the straight-support structure elastic member 22 to leave the origin position and move upward, the inner end B of the straight-support structure elastic member 22 produces an upward bending motion relative to the outer end A of the straight-support structure elastic member 22, and the straight-support structure elastic member 22 produces upward bending deformation. The displacement of the current position of the inner end B of the straight-support structure elastic member 22 relative to the position of the inner end B of the elastic member 22 in the free state is the upward deflection of the straight-support structure elastic member 22. Figure 2-4 and Figure 3-3 show the translation axis 10 leaving the origin position and moving upward along its longitudinal axis L 1The case of downward movement. Since the fixed ring 23 in the straight-support structure is fastened to the translation shaft 10, when the translation shaft 10 moves downward from the origin position, it drives the fixed ring 23 in the straight-support structure to move downward, and further drives the inner end B of the straight-support structure elastic member 22 to move downward. Since the outer end A of the straight-support structure elastic member 22 is firmly connected to the outer fixed ring 21 of the straight-support structure, and the outer fixed ring 21 of the straight-support structure is stationary relative to the lower housing of the device, therefore, the outer end A of the straight-support structure elastic member 22 is stationary relative to the lower housing of the device, and the translation shaft 10 generates relative movement relative to the outer end A of the straight-support structure elastic member 22. The straight-support structure elastic member 22 undergoes elastic bending deformation under the action of the relative movement of the translation shaft 10. More specifically, when the translation shaft 10 drives the inner end B of the straight-support structure elastic member 22 to move downward from the free state of the elastic member, the inner end B of the straight-support structure elastic member 22 generates a downward bending movement relative to its outer end A, and the straight-support structure elastic member 22 generates a downward bending deformation. The direction of this bending deformation is opposite to the direction of the bending deformation generated when the translation shaft 10 moves upward from the origin position. The displacement of the current position of the inner end B of the straight-support structure elastic member 22 relative to the position of the inner end B of the elastic member 22 in the free state is the downward deflection of the straight-support structure elastic member 22. Accordingly, when the drive shaft 10 makes a reciprocating linear motion, it drives the inner end B of the straight-support structure elastic member 22 to make an upward-downward reciprocating bending motion around the outer end A of the elastic member, and the straight-support structure elastic member 22 generates an upward-downward bending deformation.

[0049] As described above, the translation shaft 10 makes a linear reciprocating motion relative to the outer fixed ring 21 of the straight-support structure. The outer and inner ends of the straight-support structure elastic member 22, that is, the two ends A and B, are respectively fixedly connected to the outer fixed ring 21 of the straight-support structure and the fixed ring 23 in the straight-support structure. The straight-support structure elastic member 22 has the performance of a spring and is equivalent to a bending elastic member. The fixed ring 23 in the straight-support structure is fastened to the translation shaft 10 without clearance, that is, the translation shaft 10 is fastened to the B end of the straight-support structure elastic member 22 without clearance. The fixed ring 23 in the straight-support structure, the B end of the straight-support structure elastic member 22, and the translation shaft 10 have the same linear velocity. Therefore, this fixed connection without clearance can ensure that the movement noise between the translation shaft 10 and the straight-support structure 20 is very small.

[0050] Set the dimension of the straight-support structure elastic member 22 along the direction perpendicular to the driving force F 1 as width b 1 ; the dimension of the straight-support structure elastic member 22 along the direction parallel to the driving force F 1 is thickness t 1 . In an embodiment of the present invention, it is selected that b 1 is greater than three times of t 1 , that is, b 1 >3t 1When it is set that the straight - support structure elastic member 22 is subjected to a force in the circumferential tangential direction along the translation axis 10, the bending deformation section coefficient corresponding to the bending deformation generated by the straight - support structure elastic member 22 is the circumferential bending deformation section coefficient I z1 , when the straight - support structure elastic member 22 is subjected to a force in the direction parallel to the longitudinal axis L 1 of the translation axis 10 (i.e., the driving force F 1 ), the bending deformation section coefficient corresponding to the bending deformation generated by the straight - support structure elastic member 22 is the axial bending deformation section coefficient I z2 , this axial bending deformation section coefficient I z2 can also be understood as the thickness t 1 of the straight - support structure elastic member 22 in the direction of the longitudinal axis L 1 of the translation axis 10 (the direction of the driving force F 1 ). When bending deformation occurs in the force - receiving direction, it is the bending deformation section coefficient of the cross - section composed of the thickness t 1 in the direction of the longitudinal axis L 1 of the translation axis 10 and its width b 1 in the circumferential direction (perpendicular to the direction of the driving force F 1 ) of the translation axis 10. Due to the reasonable selection of the numerical ratio of b 1 and t 1 in this embodiment, the axial bending deformation section coefficient I z2 of the straight - support structure elastic member 22 can be much smaller than the circumferential bending deformation section coefficient I z1 , and the axial bending deformation section coefficient I z2 can even be less than one - ninth of the circumferential bending deformation section coefficient I z1 (I z2 < I z1 / 9). Therefore, the straight - support structure elastic member 22 not only easily responds to the reciprocating motion of the translation axis 10 along the longitudinal axis L 1 of the drive shaft to generate bending deformation, but also can hinder the rotation of the translation axis 10 around its longitudinal axis L 1 . Furthermore, the straight - support structure elastic member 22 can reliably respond to the driving force F 1 of the translation axis 10 under the drive of the reciprocating linear motion of the drive shaft 10 to generate corresponding elastic bending deformation. In the present invention, the bending deformation section is the cross - section of the straight - support structure elastic member 22 composed of t 1 and b 1 . Obviously, when the straight - support structure elastic member 22 is subjected to a force in the circumferential direction (perpendicular to the direction of the driving force F 1 ) along the translation axis 10, it is more difficult to bend.

[0051] In the present invention, the fixed ring 23 within the straight-branch structure is fixedly connected to the translation shaft 10, and the maximum amplitude of the translation shaft 10 is approximately equal to the maximum deflection of the elastic member 22 of the straight-branch structure. The maximum amplitude of the translation shaft 10 refers to the maximum displacement of the translation shaft 10 from the origin of the trajectory corresponding to the free state of the elastic member 22 of the straight-branch structure to the upper (or lower) side.

[0052] In addition, since the fixed ring 23 within the straight-branch structure is fixedly connected to the translation shaft 10, the thickness of the fixed ring 23 within the straight-branch structure along the longitudinal axis L of the translation shaft 10 1 is greater than the thickness of the elastic member 22 of the straight-branch structure in the cross-section perpendicular to the radial direction of the drive shaft along the longitudinal axis L of the translation shaft 10 1 direction (i.e., the driving force F 1 direction) of thickness t 1 , thereby ensuring a firm connection between the fixed ring 23 within the straight-branch structure and the translation shaft 10.

[0053] In the present invention, as shown in Figure 3-1 , the distance between the upper surfaces of the inner and outer fixed rings 21 and 23 of the straight-branch structure 20 and the head can be designed to be less than the distance between the upper edge of the elastic member 22 of the straight-branch structure and the head, or the distance between the lower surfaces of the inner and outer fixed rings 21 and 23 of the straight-branch structure 20 and the head can be designed to be greater than the distance between the lower edge of the elastic member 22 of the straight-branch structure and the head, so that at least one side of the upper or lower side of the cross-section of the combined straight-branch structure 20 along the longitudinal axis L parallel to the translation shaft 10 1 is concave in shape, that is, at least one side of the upper or lower side of the cross-section of the combined straight-branch structure 20 along the direction of movement of the translation shaft 10 is concave in shape.

[0054] As described above, the elastic member 22 of the straight-branch structure exhibits spring characteristics. According to the principle of the spring oscillator, the driving kinetic energy of the translation shaft 10 can be converted into the elastic potential energy of the elastic member 22 of the straight-branch structure. Similarly, the elastic potential energy of the elastic member 22 of the straight-branch structure can be converted into the driving kinetic energy of the translation shaft 10. The elastic potential energy of the elastic member 22 of the straight-branch structure and the driving kinetic energy of the translation shaft 10 are repeatedly converted, and the energy loss during the conversion is very small. When the natural frequency of the elastic system composed of the elastic member 22 of the straight-branch structure and the movement frequency of the translation shaft 10 are within the resonance range, that is, the ratio of the natural frequency of the elastic system to the movement frequency of the translation shaft 10 is 75% - 125%, the conversion of elastic potential energy and driving kinetic energy between the elastic member 22 of the straight-branch structure and the translation shaft 10 hardly generates energy loss. For this reason, the elastic member 22 of the straight-branch structure can be designed such that its cross-section perpendicular to the radial direction of the translation shaft 10 is rectangular. At this time, the equivalent spring stiffness coefficient K of the elastic member 22 of the straight-branch structure 1r = n * E * b 1r * t 1r3 / (4 * h 1r 3 ), where n is the equivalent number of the straight - support structure elastic members 22; E is the elastic modulus of the material; b 1r 、t 1r 、h 1r represent the b 1 、t 1 、h 1 of the straight - support structure elastic member 22 respectively corresponding to when the cross - section of the straight - support structure elastic member 22 is rectangular. According to the elastic oscillator principle, m 1r is the mass of the elastic system. By reasonably selecting the values of b 1r 、t 1r 、h 1r or the ratio of their values, an ideal equivalent spring stiffness coefficient K 1r can be obtained, so that the natural frequency of the elastic system composed of the straight - support structure elastic members 22 can be obtained. Furthermore, when the natural frequency of the elastic system composed of the straight - support structure elastic members 22 and the linear motion frequency of the translation axis 10 are in the resonance range, there is almost no energy loss between the straight - support structure elastic members 22 and the translation axis 10. The straight - support structure elastic member 22 can also be designed such that its cross - section perpendicular to the radial direction of the translation axis 10 is triangular. At this time, the equivalent spring stiffness coefficient K 1s = n * E * b 1s * t 1s 3 / (12 * h 1s 3 ), where n is the equivalent number of the straight - support structure elastic members 22; E is the elastic modulus of the material; b 1s 、t 1s 、h 1s represent the b 1 、t 1 、h 1 of the straight - support structure elastic member 22 respectively corresponding to when the cross - section of the straight - support structure elastic member 22 is triangular. According to the elastic oscillator principle, m 1s is the mass of the elastic system. Similarly, by reasonably selecting the values of b 1s 、t 1s 、h 1s or the ratio of their values, an ideal equivalent spring stiffness coefficient K 1r, so that the natural frequency of the elastic system composed of the straight-support structure elastic member 22 can be obtained. Furthermore, when the natural frequency of the elastic system composed of the straight-support structure elastic member 22 and the linear motion frequency of the translation axis are within the resonance range, there is almost no energy loss between the straight-support structure elastic member 22 and the translation axis 10. In addition, the natural frequency of the elastic system composed of the straight-support structure elastic member 22 can also be obtained through experiments.

[0055] Figure 4-7 shows the drive shaft 40 rotating reciprocally about its longitudinal axis L 2 relative to the lower housing of the device. In this embodiment, at least a part of the rotating shaft 40 and a rotating motion support structure 50 for supporting the rotating shaft 40 are installed in the lower housing of the device. The remaining part of the rotating shaft 40 can extend into the upper housing of the device, and a head driven by the rotating shaft 40 is also installed in the upper housing of the device. The transverse axis of the head is substantially perpendicular to the longitudinal axis L of the rotating shaft 40 2 . The rotation-support structure 50 includes a rotation-support structure outer fixing ring 51, at least one rotation-support structure elastic member 52, and a rotation-support structure inner fixing ring 53. The rotation-support structure inner fixing ring 53 is fastened to the rotating shaft 40, and there is no relative movement between them. The rotation-support structure inner fixing ring 53 rotates with the rotation of the rotating shaft 40. The rotation-support structure outer fixing ring 51 is directly or fastened to the inner side of the lower housing of the device by a rotation-support structure fixing structure 60. The rotation-support structure outer fixing ring 51 is stationary relative to the rotation-support structure fixing member 60 (when fastened by the fixing member) and the lower housing of the device. At least one rotation-support structure elastic member 52 is distributed between the rotation-support structure outer fixing ring 51 and the rotation-support structure inner fixing ring 53. As Figure 6-2 to Figure 6-4 and Figure 7-5 shown, the outer end C of the rotation-support structure elastic member 52 is firmly connected to the rotation-support structure outer fixing ring 51, and the inner end D of the rotation-support structure elastic member 52 is firmly connected to the rotation-support structure inner fixing ring 53. Figure 6-2 , Figure 7-2 and Figure 7-5 show the situation where the rotation-support structure 50 is at the origin position of the reciprocating rotation motion trajectory of the rotating shaft 40. At this time, the rotating shaft 40 rotates about its longitudinal axis L 2 with a zero deflection angle, and the rotation-support structure elastic member 52 is in a free state, and the elastic member 52 does not produce elastic bending deformation. Refer to Figure 6-3 and Figure 7-3, when the rotating shaft 40 moves away from the origin position of its reciprocating rotation trajectory in the clockwise direction, since the fixed ring 53 in the rotation-support structure is fastened to the rotating shaft 40, the inner end D of the rotation-support structure elastic member 52 is firmly connected to the fixed ring 53 in the rotation-support structure. The rotating shaft 40 drives the fixed ring 53 in the rotation-support structure to rotate in the clockwise direction. The fixed ring 53 in the rotation-support structure drives the inner end D of the rotation-support structure elastic member 52 to also rotate in the clockwise direction. And the outer end C of the rotation-support structure elastic member 52 is firmly connected to the outer fixed ring 51 of the rotation-support structure. The outer fixed ring 51 of the rotation-support structure and the outer end C of the rotation-support structure elastic member 52 are stationary relative to the lower housing of the device. The rotating shaft 40 moves relative to the outer fixed ring 51 of the rotation-support structure and the outer end C of the rotation-support structure elastic member 52. The inner end D of the rotation-support structure elastic member 52 is stationary relative to the rotating shaft 40. The rotation-support structure elastic member 52 is elastically bent and deformed under the action of the rotating shaft 40. More specifically, when the rotating shaft 40 drives the inner end D of the rotation-support structure elastic member 52 to move away from the free state of the elastic member 52 in the clockwise direction, the rotation-support structure elastic member 52 bends and deforms counterclockwise around its outer end C. The displacement of the current position of the inner end D of the rotation-support structure elastic member 52 relative to the position of the inner end D of the elastic member in the free state is the counterclockwise deflection of the elastic member 52. Refer to Figure 6-4 and Figure 7-4 , which show the situation where the rotating shaft 40 moves away from the origin position of the reciprocating rotation trajectory in the counterclockwise direction. Since the fixed ring 53 in the rotation-support structure is fastened to the rotation driving shaft 40, the rotation driving shaft 40 drives the fixed ring 53 in the rotation-support structure to move in the counterclockwise direction. And the inner end D of the rotation-support structure elastic member 52 is firmly connected to the fixed ring 53 in the rotation-support structure. The inner end D of the rotation-support structure elastic member 52 is also driven to move in the counterclockwise direction. And the outer end C of the rotation-support structure elastic member 52 is firmly connected to the outer fixed ring 51 of the rotation-support structure. The outer fixed ring 51 of the rotation-support structure is stationary relative to the lower housing of the device. The rotating shaft 40 rotates relative to the outer fixed ring 51 of the rotation-support structure. The inner end D of the rotation-support structure elastic member 52 rotates relative to the outer end C of the rotation-support structure elastic member 52. The rotation-support structure elastic member 52 is elastically bent and deformed under the action of the rotating shaft 40. More specifically, when the rotating shaft 40 drives the inner end D of the rotation-support structure elastic member 52 to move away from the free state of the elastic member 52 in the counterclockwise direction, the inner end D of the rotation-support structure elastic member 52 rotates clockwise around its outer end C. The displacement of the current position of the inner end D of the rotation-support structure elastic member 52 relative to the position of the inner end D of the elastic member 52 in the free state is the clockwise deflection of the elastic member 52.

[0056] Refer to Figure 4-7, the rotating shaft 40 drives the rotating-support structure elastic member 52 to perform reciprocating bending motion in the clockwise-counterclockwise directions around the outer end C of the elastic member 52. The rotating-support structure elastic member 52 acts as an elastic member. The inner fixing ring 53 of the rotating-support structure is fastened to the rotating shaft 40, and the inner fixing ring 53 of the rotating-support structure and the rotating shaft 40 have the same angular velocity. The rotating shaft 40 and the inner fixing ring 53 of the rotating-support structure are fastened and connected without clearance, and the rotating shaft 40 is equivalently connected to the rotating-support structure elastic member 52 without clearance. Set the dimension of the rotating-support structure elastic member 52 along the radial direction of the rotating shaft 40 as the length h 2 , the dimension of the rotating-support structure elastic member 52 along the direction perpendicular to the driving force F 2 is the width b 2 , the dimension of the rotating-support structure elastic member 52 along the direction parallel to the driving force F 2 is the thickness t 2 , preferably b 2 > 3t 2 . When it is set that the rotating-support structure elastic member 52 generates bending deformation under the force in the circumferential tangent direction of the rotating shaft 40, the corresponding bending deformation section modulus of the rotating-support structure elastic member 52 is the circumferential bending deformation section modulus I z3 , the circumferential bending deformation section modulus I z3 can also be understood as the circumferential bending deformation section modulus I of the cross-section composed of b 2 and t 2 when the rotating-support structure elastic member 52 is under the force in the circumferential tangent direction of the rotating shaft 40 z3 . When it is set that the rotating-support structure elastic member 52 is under the force in the direction parallel to the longitudinal axis L 2 of the rotating shaft 40, the bending deformation section modulus corresponding to the bending deformation generated by the rotating-support structure elastic member 52 is the axial bending deformation section modulus I z4 , and the axial bending deformation section modulus I z4 can also be understood as the axial bending deformation section modulus I of the cross-section composed of b 2 and t 2 when the rotating-support structure elastic member 52 is under the force in the direction parallel to the longitudinal axis L 2 of the rotating shaft 40 z4 . Since the numerical ratio of b 2 and t 2 is reasonably selected in the present invention, b 2 > 3t 2 , so that the axial bending deformation section modulus I z4 of the rotating-support structure elastic member 52 is much greater than the circumferential bending deformation section modulus I z3 , and the circumferential bending deformation section modulus I z3 can even be less than the axial bending deformation section modulus I z4One-ninth of (I z3 <I z4 / 9). Therefore, driven by the reciprocating rotational motion of the drive shaft 40, the swivel-support structure elastic member 52 can reliably respond to the driving force of the rotating shaft 40 to produce elastic bending deformation. In the present invention, the bending deformation cross-section is the cross-section of the swivel-support structure elastic member 52 composed of b 2 and t 2 . Obviously, under the action of the force in the circumferential direction of the rotating shaft 40, the swivel-support structure elastic member 52 is relatively easy to bend. Thus, driven by the reciprocating rotational motion of the drive shaft 40, the swivel-support structure elastic member 52 can reliably respond to the driving force of the rotating shaft 40 to produce elastic bending deformation.

[0057] In this embodiment, the swivel-support structure inner fixing ring 53 is fixedly connected to the rotational motion drive shaft 40. The maximum clockwise (or counterclockwise) rotation angle that the rotational motion drive shaft 50 reaches when leaving the trajectory point corresponding to the elastic member 52 in the free state is approximately equal to the maximum counterclockwise (or clockwise) rotation angle of the swivel-support structure elastic member 52.

[0058] The following further takes an electric toothbrush and a dental irrigator as examples and combines with the attached Figure 8-10 to describe other exemplary embodiments of the present invention. Although only the electric toothbrush and the dental irrigator are taken as examples for explanation below, the present invention is not limited thereto. The present invention is also applicable to other electric cleaning and care appliances having a reciprocating drive shaft, such as a facial cleansing device, a shaver, etc.

[0059] Figure 8 For an electric toothbrush equipped with a reciprocating linear motion combination as Figure 1 shown, Figure 9 For an electric toothbrush equipped with a reciprocating rotational motion combination as Figure 4 shown, Figure 10 For a dental irrigator equipped with a reciprocating linear motion combination as Figure 1 shown.

[0060] As Figure 8 shown, the drive shaft (translation shaft) 10 of the electric toothbrush that makes a reciprocating linear motion is arranged in the lower handle housing S-1 and extends into the upper handle housing S-2. The upper handle housing S-2 is also equipped with a brush head driven by the translation shaft 10. The brush head is distributed with bristles S-3 for cleaning teeth. The axis L 3 of the bristles S-3 is 1 substantially perpendicular to the longitudinal axis L of the translation shaft 10. Figure 10In the illustrated embodiment, the translation shaft 10 is disposed in the lower shell C-1 of the oral irrigator, and the rinsing head is installed in the rinsing head shell C-2, and the rinsing liquid driven by the translation shaft 10 flows out through the rinsing head. For this type of electric cleaning and care appliance, the maximum amplitude of the translation shaft 10 is relatively small, about 2 mm. Therefore, the straight-branch structure 20 of the present invention is particularly suitable for electric cleaning and care appliances in which the maximum amplitude of the translation shaft 10 is less than 3 mm. More specifically, the straight-branch structure 20 of the present invention is suitable for electric cleaning and care products in which the total displacement of the translation shaft 10 from top to bottom is less than 6 mm. In order to be durable, it is usually hoped that the drive shaft of the electric cleaning and care product can withstand more than 100,000 reciprocating motions. To this end, the straight-branch structure elastic member 22 is set to a length h in the radial direction of the translation shaft 10. 1 Designed to be larger than the longitudinal axis L of the straight-branch structure elastic member 22 along the translation shaft 10 1 Direction (i.e. driving force F 1 direction) thickness t 1 Three times, that is, h 1 >3t 1 To ensure that the straight-branch structure elastic member 22 can reliably achieve reciprocating bending deformation during the life cycle of the electric cleaning and care appliance. The applicant has further concluded through a large number of tests that the straight-branch structure elastic member 22 along the longitudinal axis L of the translation shaft 10 1 Direction (driving force F 1 Direction) dimension t 1 The value range of is preferably 0.1mm-1.3mm. More preferably, the straight-branch structure elastic member 22 is along the longitudinal axis L of the translation shaft 10. 1 Direction (driving force F 1 direction) thickness t 1 The value range is 0.2mm-0.7mm.

[0061] exist Figure 8 In the embodiment shown, the pressure exerted by the teeth on the bristles S-3 is substantially perpendicular to the longitudinal axis L of the translation shaft 10. 1 The pressure exerted by the teeth on the bristles S-3 is equivalent to the straight-branch structure elastic member 22, which is also equivalent to applying a force (pressure or tension) in the direction from the inner end B to the outer end A of the straight-branch structure elastic member 22. According to Newton's third law, the straight-branch structure elastic member 22 will generate a resistance force to resist the pressure (or tension) exerted by the teeth on the bristles S-3, and the combined force direction of the resistance force is roughly perpendicular to the longitudinal axis L of the translation axis. 1 , and is in the opposite direction to the pressure exerted by the teeth on the bristles S-3. Therefore, the straight-branch structure elastic member 22 constrains the radial movement of the translation shaft 10, and the straight-branch structure elastic member 22 constrains the translation shaft 10 to move in a direction perpendicular to its longitudinal axis L. 1In the direction of movement, the straight-support structure elastic member 22 forms a support for the translation shaft 10 in the radial direction of the translation shaft 10. Since the straight-support structure elastic member 22 forms a support for the drive shaft 10 in the radial direction of the translation shaft 10, the direction of the support force generated by the straight-support structure elastic member 22 is 90 degrees to the movement displacement direction of the translation shaft 10, and the inner fixed ring 23 of the straight-support structure is fixedly connected to the translation shaft 10. There is no need to overcome friction to do work between the inner fixed ring 23 of the straight-support structure and the translation shaft 10. Therefore, the support of the straight-support structure 20 for the drive shaft 10 in the radial direction of the translation shaft 10 does not cause energy loss.

[0062] In the present invention, the straight-support structure 20 can not only restrict the radial movement of the translation shaft 10, but also effectively support the translation shaft 10. Moreover, the translation shaft 10 and the inner fixed ring 23 of the straight-support structure 20 are connected without clearance, thereby avoiding the impact and collision of the translation shaft 10 on the straight-support structure 20 and greatly reducing the noise. In addition, the energy loss of the reciprocating conversion between the elastic potential energy of the straight-support structure elastic member 22 and the driving kinetic energy of the translation shaft 10 is very small.

[0063] See Figure 9 , the drive shaft 40 that makes a reciprocating rotational movement of the electric toothbrush is arranged in the lower handle housing S-4 and extends into the upper handle housing S-5. A brush head driven by the drive shaft 40 is also installed in the upper handle housing S-5. Bristles S-6 for cleaning teeth are distributed on the brush head. The axis L of the bristles S-6 4 is substantially perpendicular to the longitudinal axis L of the rotating shaft 40 2 . For electric cleaning and care appliances such as electric toothbrushes, the rotation angle amplitude of the rotating shaft 40 is relatively small, about 25 degrees. Therefore, the rotation-support structure 50 of the present invention is suitable for electric cleaning and care appliances in which the maximum rotation angle amplitude of the rotating shaft 40 is less than 40 degrees. More specifically, the rotation-support structure 50 of the present invention is suitable for electric cleaning and care appliances in which the total rotation angle of the rotating shaft 40 is less than 80 degrees. The total rotation angle of the rotating shaft 40 is twice the maximum rotation angle amplitude. It can also be understood that the total rotation angle of the rotating shaft 40 is the angle swept from the leftmost to the rightmost away from the rotation center. For durability, it is generally desired that the drive shaft of the electric cleaning and care appliance can withstand more than 100,000 reciprocating movements. For this reason, in another embodiment of the present invention, the rotation-support structure elastic member 52 is arranged such that its length h in the radial direction of the rotating shaft 40 2 is greater than three times the thickness t of the elastic member 52 in the direction parallel to the driving force F of the rotating shaft 40 2 , that is, h 2 > 3t 2 2, to ensure that the rotation-support structure elastic member 52 can reliably reciprocally bend and deform during the life cycle of the electric cleaning and care product. Through a large number of tests, the applicant further found that preferably, the thickness t of the rotation-support structure elastic member 52 in the circumferential direction of the rotation axis 40 2 has a value range of 0.1 mm - 1.3 mm. More preferably, the t 2 has a value range of 0.2 mm - 0.7 mm.

[0064] On the contrary, in the existing shaft-hole fitting structure, a driving shaft that makes a reciprocating motion (a driving shaft that makes a reciprocating rotational motion or a driving shaft that makes a reciprocating linear motion) passes through a shaft sleeve. Generally, there is a movement gap of 0.01 mm - 0.03 mm between the shaft sleeve and the driving shaft that makes a reciprocating motion. The shaft sleeve restricts the radial movement of the driving shaft and supports the driving shaft. Due to the existence of the above-mentioned movement gap and the characteristic that the shaft sleeve restricts the radial movement of the driving shaft, when an irregular force is applied to the bristles by the teeth, an irregular radial force is applied to the driving shaft. This radial force will cause impacts and collisions between the driving shaft and the shaft sleeve, and the said impacts and collisions can cause relatively large irregular noises. On the other hand, since the shaft sleeve restricts the radial movement of the driving shaft and supports the driving shaft, when a radial force is applied to the driving shaft, the driving shaft contacts the shaft sleeve, and the shaft sleeve supports the driving shaft to overcome the radial force applied to the driving shaft, and friction is generated between the driving shaft and the shaft sleeve. The said frictional force will hinder the movement of the driving shaft, thereby consuming energy.

[0065] In summary, compared with the existing support structure, the support structure for the driving shaft that makes a reciprocating rotational motion or a reciprocating linear motion provided by the present invention, on the one hand, because there is no clearance connection between the reciprocating motion driving shaft and the support structure, it avoids the impacts and collisions on the support structure caused by the reciprocating motion of the driving shaft, greatly reducing the noise. On the other hand, the energy loss during the conversion between the elastic potential energy of the support structure elastic member and the driving kinetic energy of the driving shaft is very small. Therefore, it has the advantages of simple structure, low noise, and small energy loss. In addition, the support structure is preferably made of plastic parts, with low cost and suitable for mass production.

Claims

1. A support structure, characterized in that, The support structure supports a translation shaft (10) that reciprocates linearly along its first longitudinal axis (L 1 ). At least a portion of the translation shaft (10) is located within a stationary device lower housing. Under the action of a reciprocating linear motion driving force (F 1 ), the translation shaft (10) reciprocates linearly along its first longitudinal axis (L 1 ) relative to the device lower housing. The stationary device upper housing includes a head driven by the translation shaft (10). A first transverse axis (L 3 ) of the head is perpendicular to the first longitudinal axis (L 1 ) of the translation shaft (10). The device lower housing further includes a linear motion support structure (20) for supporting the translation shaft (10). The linear motion support structure (20) includes a linear motion support structure inner fixing ring (23), at least one linear motion support structure elastic member (22), and a linear motion support structure outer fixing ring (21). The linear motion support structure inner fixing ring (23) is fastened to the translation shaft (10) along the circumferential direction of the translation shaft (10). The linear motion support structure outer fixing ring (21) is directly or indirectly fastened to the inner wall of the device lower housing. The linear motion support structure elastic member (22) has the properties of a spring and is distributed between the linear motion support structure outer fixing ring (21) and the linear motion support structure inner fixing ring (23). the first outer end (A) of the linear motion support structure elastic member (22) is fixedly connected to the outer fixed ring (21) of the linear motion support structure, and the first inner end (B) of the linear motion support structure elastic member (22) is fixedly connected to the inner fixed ring (23) of the linear motion support structure; The linear motion support structure elastic member (22) is set to move perpendicularly to the reciprocating linear motion driving force (F 1 ) direction is the first width b 1 , along the direction parallel to the reciprocating linear motion driving force (F 1 ) direction is the first thickness t 1 The linear motion support structure elastic member (22) is arranged perpendicular to the reciprocating linear motion driving force (F 1 ) direction of the first width b 1 Greater than the driving force (F 1 ) direction of the first thickness t 1 Three times, that is, b 1 >3t 1 , and setting a first length h of the linear motion support structure elastic member (22) along the radial direction of the translation axis (10) 1 greater than the elastic member (22) along the direction parallel to the reciprocating linear motion driving force (F 1 ) direction first thickness t 1 Three times, that is, h 1 >3t 1 , the first thickness t 1 is 0.1-1.3 mm, so that the axial bending deformation section coefficient I of the elastic member z2 Less than the circumferential bending deformation section coefficient I z1 One ninth of I z2 <I z1 / 9, and the natural frequency of the elastic system formed by the elastic member (22) and the movement frequency of the translation shaft (10) are within a resonance range, so that the energy conversion loss between the elastic potential energy of the elastic member (22) and the driving kinetic energy of the translation shaft (10) is reduced.

2. A support structure, characterized in that, The support structure supports a rotating shaft (40) that reciprocally rotates about its second longitudinal axis (L 2 ) relative to the lower housing of the device. At least a portion of the rotating shaft (40) is located within the stationary lower housing of the device. Under the action of the reciprocating rotation driving force (F 2 ), the rotating shaft (40) reciprocally rotates about its second longitudinal axis (L 2 ) relative to the lower housing of the device. The stationary upper housing of the device includes a head driven by the rotating shaft (40). The second transverse axis (L 4 ) of the head is perpendicular to the second longitudinal axis (L 2 ) of the rotating shaft (40). The lower housing of the device further includes a rotational movement support structure (50) for supporting the rotating shaft. The rotational movement support structure (50) includes an inner fixing ring (53) of the rotational movement support structure, at least one elastic member (52) of the rotational movement support structure, and an outer fixing ring (51) of the rotational movement support structure. The inner fixing ring (53) of the rotational movement support structure is fastened to the rotating shaft (40) along the circumferential direction of the rotating shaft (40). The outer fixing ring (51) of the rotational movement support structure is directly or indirectly fastened to the inner wall of the lower housing of the device. The elastic member (52) of the rotational movement support structure has the properties of a spring and is distributed between the outer fixing ring (51) of the rotational movement support structure and the inner fixing ring (53) of the rotational movement support structure. wherein, the second outer end (C) of the rotary motion support structure elastic member (52) is fixedly connected to the outer fixed ring (51) of the rotary motion support structure, and the second inner end (D) of the rotary motion support structure elastic member (52) is fixedly connected to the inner fixed ring (53) of the rotary motion support structure; Among them, it is set that the dimension of the elastic member (52) of the rotary motion support structure along the direction perpendicular to the reciprocating rotary motion driving force (F 2 ) is the second width b 2 , and the dimension of the elastic member (52) of the rotary motion support structure along the direction parallel to the reciprocating rotary motion driving force (F 2 ) is the second thickness t 2 , and the second width b 2 of the elastic member (52) of the rotary motion support structure along the direction perpendicular to the reciprocating rotary motion driving force (F 2 is greater than three times its second thickness t 2 along the direction parallel to the reciprocating rotary motion driving force (F 2 ), that is, b 2 > 3t 2 , and it is set that the second length h 2 of the elastic member (52) of the rotary motion support structure along the radial direction of the rotary shaft (40) is greater than three times the second thickness t 2 of the elastic member (52) along the direction parallel to the reciprocating rotary motion driving force (F 2 ), that is, h 2 > 3t 2 , the second thickness t 2 is 0.1 - 1.3 mm, so that the circumferential bending deformation section coefficient I z3 of the elastic member is less than one-ninth of the axial bending deformation section coefficient I z4 , that is, I z3 < I z4 / 9, and the natural frequency of the elastic system formed by the elastic member (52) and the motion frequency of the rotary shaft (40) are in the resonance range, so that the energy conversion loss between the elastic potential energy of the elastic member (52) and the driving kinetic energy of the rotary shaft (40) is reduced.

3. The support structure according to claim 1, wherein, the outer fixed ring (21) of the linear motion support structure, the linear motion support structure elastic member (22), and the inner fixed ring (23) of the linear motion support structure are all made of plastic.

4. The support structure according to claim 2, wherein, the outer fixed ring (51) of the rotary motion support structure, the rotary motion support structure elastic member (52), and the inner fixed ring (53) of the rotary motion support structure are all made of plastic.

5. The support structure according to claim 3, wherein, the outer fixed ring (21) of the linear motion support structure, the linear motion support structure elastic member (22), and the inner fixed ring (23) of the linear motion support structure are made of thermoplastic.

6. The support structure according to claim 4, wherein, the outer fixed ring (51) of the rotary motion support structure, the rotary motion support structure elastic member (52), and the inner fixed ring (53) of the rotary motion support structure are made of thermoplastic.

7. The support structure according to claim 3, wherein, the inner fixed ring (23) of the linear motion support structure and the translation shaft (10) are injection-molded into an integral part.

8. The support structure according to claim 4, wherein, the inner fixed ring (53) of the rotary motion support structure and the rotary shaft (40) are injection-molded into an integral part.

9. The support structure according to claim 1, wherein, the linear motion support structure elastic member (22) is integrally connected to the inner fixed ring (21) and the outer fixed ring (23) of the linear motion support structure (20).

10. The support structure according to claim 2, wherein, the rotary motion support structure elastic member (52) is integrally connected to the inner fixed ring (53) and the outer fixed ring (51) of the rotary motion support structure (50).

11. The support structure according to claim 9, wherein, The elastic member (22) of the linear motion support structure has a first thickness t along a direction parallel to the reciprocating linear motion driving force (F 1 ) and is 0.2 mm - 0.7 mm. 1 ​ 12. The support structure according to claim 10, wherein, The elastic member (52) of the rotational movement support structure has a second thickness t 2 in the direction parallel to the reciprocating rotational movement driving force (F 2 ) and is 0.2 mm to 0.7 mm.

13. The support structure according to claim 1, wherein, The electric cleaning and care appliance is an electric toothbrush or a dental irrigator, and the support structure is a linear motion support structure (20) for supporting a translation shaft (10) that reciprocates linearly along the first longitudinal axis (L 1 ).

14. The support structure according to claim 13, wherein, The distance between the upper surfaces of the inner fixing ring (23) and the outer fixing ring (21) of the linear motion support structure (20) and the head is less than the distance between the upper edge of the elastic member (22) of the linear motion support structure and the head, or the distance between the lower surfaces of the inner fixing ring (23) and the outer fixing ring (2123) of the linear motion support structure (20) and the head is greater than the distance between the lower edge of the elastic member (22) of the linear motion support structure and the head, so that at least one of the upper and lower sides of the cross-section of the combined linear motion support structure (20) along the first longitudinal axis (L 1 ) parallel to the translation axis (10) is concave in shape.

15. The support structure according to claim 13, wherein, Under the action of the reciprocating linear motion driving force (F 1 ), the translation shaft (10) moves along its first longitudinal axis (L 1 ) with a maximum motion amplitude of less than 3 mm.

16. The support structure according to claim 15, wherein, The translational axis (10) has a maximum movement amplitude of 2 mm along its first longitudinal axis (L 1 ).

17. The support structure according to claim 2, wherein, The electric cleaning and care appliance is an electric toothbrush, and the support structure is a rotary motion support structure (50) for supporting a rotary shaft (40) that reciprocally rotates about the second longitudinal axis (L 2 ).

18. The support structure according to claim 17, wherein, Under the action of the reciprocating rotational driving force (F 2 ), the maximum rotational angle amplitude of the rotating shaft (40) about its second longitudinal axis (L 2 ) is less than 40 degrees.

19. The support structure according to claim 18, wherein, The rotation axis (40) has a maximum rotation angle amplitude of 25 degrees about its second longitudinal axis (L 2 ).

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