Pivoting drive mechanism for a massage device

Abstract

A pivot drive mechanism for a massager, comprising: a support member, a pivot arm, a transmission member, and a motor; wherein the support element is connected to a first support portion, the first support portion is connected to and supports the pivot arm to form a plurality of support points, the plurality of support points being arranged in a circular array around a rotation axis of the motor, and the pivot arm being rotatable in any direction around the center of the plurality of support points; wherein the transmission element comprises a first transmission section and a second transmission section; wherein the first transmission section is connected to an output shaft of the motor so that the transmission element rotates with the output shaft of the motor; wherein the second transmission section bears against the pivot arm and drives it in the direction of rotation of the motor; Furthermore, the second transmission section rotates relative to the swivel arm; Furthermore, an abutment position between the second transmission section and the pivot arm is configured such that a longitudinal direction of the pivot arm maintains a fixed included angle with the output shaft of the motor.

Description

TECHNICAL FIELDThe present invention relates to a pivotal drive mechanism for a massager.BACKGROUNDDuring the continuous operation of a massage device, squeezing and rubbing processes repeatedly occur between the carrier body of the massage head and the inner wall of the flexible layer. Over time, the lubricant originally applied between the contact surfaces of these two components is gradually consumed and displaces, with a large amount of the lubricant changing to other, less critical areas. This phenomenon directly leads to a great increase in friction between the supporting body of the massage head and the inner wall of the flexible layer, possibly leading to the blocking of the transmission structure. At the same time, this can cause overloading of the motor and thus impair normal operation and the service life of the massage device.CONCRETE EMBODIMENTSTo solve the above problems of the related art, the present invention provides a pivoting drive mechanism for a massager, including: a support member, a pivot arm, a transmission member, and a motor;the support member is connected to a first support portion, the first support portion is connected to and supports the swing arm to form a plurality of support points; the plurality of support points are arranged in a circular array about a rotation axis of the motor, and the swing arm is rotatable about the center of the plurality of support points in an arbitrary direction;the transmission member includes a first transmission portion and a second transmission portion;the first transmission portion is connected to an output shaft of the motor so that the transmission member rotates together with the output shaft of the motor;wherein the second transmission portion abuts the swing arm and moves the same in the rotational direction of the motor;further, the second transmission portion rotates relative to the swing arm;Further, the abutting position between the second transmission portion and the swing arm is configured such that the longitudinal direction of the swing arm maintains a fixed inclusion angle with the output shaft of the motor.The advantageous effect of the present invention is that the relative rotational friction originally occurring between the carrier body and the flexible layer is transmitted to the second transmission section and the pivot arm. Both the pivot arm and the second transmission section can consist of metal or plastic parts and have a significantly smaller contact surface than that between the carrier body and the flexible layer, as a result of which very little friction arises. As a result, overloading of the motor can be effectively avoided and the stability and service life of the device can be improved.BRIEF DESCRIPTION OF THE DRAWINGSFIG. 1 is a schematic structural diagram of a pivoting drive mechanism for a massage device according to the related art. FIG. 2 is a structural perspective view of the pivoting drive mechanism for a massage device provided with the present invention. FIG. 3 is a perspective structural view of the pivoting drive mechanism for a massage device having a first support portion in the form of a ball structure. FIG. 4 is a sectional structural view of the pivoting drive mechanism for a massager according to a first embodiment of the first support portion. FIG. 5 is a perspective structural view of the pivoting drive mechanism for a massage device including a second embodiment of the first support portion. FIG. 6 is a sectional structural view of the pivotal drive mechanism for a massager including a third embodiment of the first support portion. FIG. 7 is a schematic structural diagram of a transmission member and a third guide part. FIG. 8 is a schematic structural diagram of another transmission member and a third guide part. FIG. 9 is a vertical sectional structural view of the pivotal drive mechanism for a massager having a spherical configuration of the first support portion. FIG. 10 is a sectional structural view of the swing arm.DETAILED DESCRIPTION OF PREFERRED EMBODIMENTSEMBODIMENT 1Embodiment 1Referring to FIGS. 1 to 10.A pivoting drive mechanism for a massage device is provided, comprising: a support member 1, a pivot arm 2, a transmission member 3, and a motor 4.The support element 1 is connected to a first support section 11. The first support portion 11 is connected to and supports the swing arm 2 so that a plurality of support points are formed. The plurality of support points are arranged in a circular array about the rotation axis of the motor 4. The swing arm 2 is rotatable about the center of these plural support points in an arbitrary direction.The transmission element 3 comprises a first transmission section 31 and a second transmission section 32.The first transmission portion 31 is connected to the output shaft of the motor 4 so that the transmission member 3 rotates together with the output shaft of the motor 4.The second transmission portion 32 abuts against the swing arm 2 in both the rotational direction and the radial direction of the output shaft of the motor 4.The pressing force acting in the rotational direction of the output shaft of the motor 4 presses the swing arm 2 to rotate about the rotational axis of the motor 4. the pressing force acting in the radial direction causes the longitudinal direction of the swing arm 2 to maintain a fixed inclusion angle with the output shaft of the motor 4. In addition, the second transmission portion 32 rotates relative to the swing arm 2.The motor 4 is in particular a geared motor comprising a drive part and a gear, so that the motor 4 can drive the swing arm 2 at a suitable speed.Referring to Fig. 1, massage devices currently available on the market include a massage head that performs a conical motion. The conical movement means that the axis of the massage head describes a cone. In such massage devices, the transmission mechanism is very simple: the output shaft of the motor 4 is directly connected to the carrier body 26 of the massage head (hereinafter, the carrier body 26 is always referred to as the carrier body of the massage head). The axis of the supporting body 26 forms an angle with the axis of the motor 4, and the extension lines of the output shaft of the motor 4 and the axis of the supporting body 26 span a vectorial triangular plane. Rotation of the output shaft of the motor 4 drives this vector plane to rotate, thereby creating a conical path.Although the prior art transmission structure seems to be fail-free per se, the outer surface of the support body 26 must be additionally covered with a silicone layer as a flexible layer in order to improve massage comfort and to make the massage head waterproof and easy to clean. In this case, the existing transmission structure interferes with the flexible layer in the fully assembled massager. In the transmission structure of the prior art, the support body 26 not only performs a conical movement but also rotates about its own axis. Since the support body 26 is firmly connected to the output shaft of the motor 4, it forcibly rotates with the rotation of the motor 4, on the other hand, as an integral component completely surrounding the massage head, the flexible layer must remain stationary in order to be gripped and used. Therefore, the flexible layer must not rotate with it. To enable this, the flexible layer and the supporting body 26 must be rotatably connected to each other, and the friction between them must be minimized as much as possible.At present, the friction is mainly reduced by applying lubricating oil to the contact surface between the flexible layer and the support body 26. However, since the silicone material is flexible, the inner wall of the flexible layer easily deforms during the repeated movement of the support body 26. Under pressure, the lubricating oil may migrate to other, non-critical areas, resulting in a continuous reduction in lubrication at the contact surface between the flexible layer and the support body 26. Moreover, the lubricating oil evaporates with the lapse of time and is consumed. If sufficient lubricating oil is no longer present at the contact surface between the flexible layer and the carrier body 26, the rotational resistance of the carrier body 26 increases considerably. This may result in the support body 26 co-rotating the flexible layer by friction, which in turn may result in deformation and compression of the flexible layer, overloading the motor or even breakage at the connection between the support body 26 and the output shaft of the motor 4.To solve this problem, the present application provides a novel drive mechanism with which the carrier body 26 can execute a conical movement.First, the mechanism includes the support member 1 and the swing arm 2. The front end of the swivel arm 2 can serve directly as the carrier body 26 of the massage head. The central portion of the swing arm 2 is connected to the first support portion 11. At the rear end inside the support element 1, a transmission element 3 is arranged. The transmission member 3 includes at least a first transmission portion 31 and a second transmission portion 32. The second transmission portion 32 is arranged eccentrically relative to the first transmission portion 31 and abuts the pivot arm 2 in the rotational direction.The first support portion 11 is connected to the swing arm 2, but does not limit its swing freedom. The pivot arm 2 is capable of pivoting in any direction, i.e. of carrying out a 360 degree pivoting. The first support portion 11 forms a plurality of support points distributed in a circular array about the rotation axis of the motor 4. For example, the first support portion 11 may have a hole structure, the edge of the hole opening serves as support points, and the hole is disposed coaxially with the motor 4. If the first support portion 11 has a flexible structure, it may be directly fixedly connected to the swing arm 2. During the movement, the swing arm 2 deforms the flexible first support portion 11 having a maximum deformation limit. The edge of this deformation portion forms a circular configuration around the rotation axis of the motor 4.The manner in which the transmission element 3 bears against the pivot arm 2 can be configured in particular as follows:The distal end of the swing arm 2 functions as the third transmission portion 21, and the transmission member 3 may be configured as a disk (any shape is possible, a round structure is simple) in which two holes are formed. One of the holes is located on the central axis of the disc and functions as the first transmission portion 31, while the other eccentrically arranged hole functions as the second transmission portion 32. The distal end of the pivot arm 2, i.e. the third transmission section 21, can be designed as a cylindrical body which is inserted directly into the second transmission section 32.Alternatively, the transmission element 3 can be configured as a Z-shaped rod having two parallel arms. One of them is connected to the output shaft of the motor 4 and serves as the first transmission portion 31, the other serves as the second transmission portion 32. Various shaft-hole configurations may serve as structures for the first transmission portion 31, the second transmission portion 32, and the third transmission portion 21.Furthermore, the transmission element 3 can be designed as a slot-shaped body, for example as a V-shaped groove or a C-shaped groove, wherein the opening is directed away from the axis of rotation of the motor 4. The third transmission section 21 is designed as a cylindrical body. In a V-shaped groove, the third transmission portion 21 is inserted into the opening of the groove. The intersection portion of the V-shaped groove prevents the third transmission portion 21 from pivoting in the direction of the rotation axis, thereby preventing the pivot arm 2 from becoming parallel to the rotation axis. Thus, the swing arm 2 maintains a fixed angle of confinement with the output shaft of the motor 4. When the motor rotates the entire V-shaped groove, the wall of the opening of the V-shaped member presses the third transmission portion 21 to rotate about the rotation axis.In the aforementioned connection configurations, the second transmission portion 32 and the third transmission portion 21 are not connected to each other and do not rotate synchronously (here, "rotation" denotes rotation about the own axis). The second transmission portion 32 rotates following the first transmission portion 31. However, the friction between the second transmission section 32 and the third transmission section 21 is minimal, so that the third transmission section 21 (and thus the entire pivot arm 2) does not rotate with it. As a result, the flexible layer can oscillate synchronously with the carrier body 26 without a relative rotation taking place. The conical path generated by the movement of the swivel arm 2 is not formed by rotation, but by the second transmission section 32 driving the swivel arm 2 continuously at different angles to an arcuate swivel movement.This embodiment provides a plurality of specific structures for the first support portion 11.The first support portion 11 may be formed as a cover of flexible material (e.g. rubber, silicone) and is connected to the front end of the support member 1. The swing arm 2 passes through the first support portion 11. In this case, the edge of the through hole through which the swing arm 2 passes serves as a support point. The swing arm 2 presses against the support point, whereby the first support portion 11 deforms to accommodate the swing motion. The swing arm 2 may be directly bonded to the first support portion 11, or the swing arm 2 may be provided with two axial restriction parts protruding in the radial direction. The first support portion 11 is located between these two axial restricting parts, thereby preventing relative sliding between the swing arm 2 and the first support portion 11.Moreover, the first support portion 11 can be simplified to a plurality of flexible strips, for example four rubber strips which are arranged in a cruciform manner. One end of each rubber strip is connected to the support member 1, the other end is connected to the side wall of the swing arm 2. When the pivot arm 2 moves towards one of the rubber strips, the support point is formed by the location at which the opposite rubber strip is connected to the pivot arm. The front and rear ends of the swing arm 2 swing in opposite directions.Alternatively, the first support portion 11 may be formed as a non-deformable thin plate having a bore formed therein. The axis of the bore is coaxial with the axis of the motor 4. A typical deep bore would support the pivot arm at two points, form a straight line and thus prevent pivoting movement. In the case of a very flat bore, on the other hand, the two support points are so close together that they effectively merge into a single support point. A straight line through a single point enables a 360 degree pivoting movement. Further, since a flat bore does not prevent the cylindrical body from swinging, the swing arm 2 can freely move within the bore of the first support portion 11. In addition, the pivot arm 2 should be provided with circumferential limiting elements in order to prevent axial sliding.Specifically, the maximum circumferential gap between the round hole and the circumferential wall of the third transmitting portion 21 is referred to as L 1, and the thickness of the thin plate (i.e., the depth of the hole) is referred to as L 2. L1 and L2 satisfy the relationship: Actually, L1 and L2 correspond to the two vertices of a right triangle. When L1 is equal, the swing arm 2 may form an angle of inclusion of 30 degrees to the rotation axis. The smaller L1, the smaller the possible angle.The present application displaces the relative rotational friction originally occurring between the support body 26 and the flexible layer to the contact point between the second transmission portion 32 and the third transmission portion 21. This greatly reduces friction, effectively preventing overloading of the motor 4 and improving the stability and durability of the apparatus.In addition, rolling friction may be introduced between the second transmission portion 32 and the third transmission portion 21, for example, by a ball structure 34. the balls may be embedded in the circumferential wall of the second transmission portion 32, whereby the sliding friction between the second transmission portion 32 and the third transmission portion 21 is converted into rolling friction, which further reduces the resistance. The ball structure 34 can be designed as a bearing. In this embodiment, the second transmission section 32 serves as a shaft and the third transmission section 21 as a bore; the bearing can either be placed over the outer surface of the second transmission section 32 or embedded in the third transmission section 21.The ball structure 34 can also be designed as independent balls. This configuration is simpler, but does not use standardized components. When implemented in the form of individual balls, the ball structure 34 may be embedded only in the shaft-like second transmitting portion 32 or the third transmitting portion 21, the balls abutting against the inner wall of the bore-like second or third transmitting portion.The front end of the swinging arm 2 is configured as a supporting head 26 for supporting the flexible layer, and a functional module 5 is provided inside the supporting head 26. Most massage heads used in massage devices have vibration and heating functions. In this embodiment, the vibration and heating functions are realized by arranging the functional module 5 in the carrier head. Since the carrier body 26 in the present application no longer carries out a relative movement with respect to the flexible layer, the flexible layer can be completely bonded to the carrier body 26. As a result, the vibration and heat generated by the functional module 5 can be transmitted to the outer surface of the flexible layer, which improves the massage effect of the device.Embodiment 2Referring to FIGS. 2 and 7.The central portion along the longitudinal direction of the swing arm 2 protrudes radially and forms a second support portion 22, the wall surface of which is formed in a spherical shape.The first support portion 11 has a hole structure, and the wall of the bore is also spherical. The axis of the first support portion 11 is oriented coaxially with the rotation axis of the motor 4.The center of the ball of the second support portion 22 is located on the axis of the first support portion 11.Embodiment 1 describes the first support portion 11 in the form of a flexible plate. In contrast, the present embodiment provides a fourth preferred structural configuration for the first support portion 11.In the structure having the flexible plate as the first support portion 11, the swing arm 2 needs to continuously compress the first support portion 11 during its movement. Since the first support portion 11 serves as a fulcrum for the swing arm 2, a certain mechanical strength is required. Accordingly, a considerable force is required to deform the first support portion 11, and this force must be applied from the motor 4. As a result, a more powerful motor 4 is required. More importantly, such a structure significantly shortens the operating time of the device due to the increased energy consumption.Moreover, the continuous compression of the flexible material may lead to cracks at the joints between the support member 1, the pivot arm 2 and the first support portion 11, which in turn may lead to failure of the first support portion 11. Therefore, highly reliable adhesives are required to ensure durability of the device.On the other hand, the configuration of the first support portion 11 as a thin rigid plate tends to be unstable in movement and generates sensible noise.To solve these problems, the present embodiment provides a more stable and reliable structure for the first support portion 11.The first support section 11 is configured as a spherical bore and the second support section 22 protrudes radially from the pivot arm 2. The wall surface of the second support portion 22 is spherical and is disposed inside the first support portion 11 so as to form a spherical fitting surface. When the ball center of the first support portion 11 is taken as a rotation center, the swing arm 2 is free to rotate about this point by the spherical fit.Compared to a hole-and-shaft fit, in which the direction of the bore determines the direction of the shaft and both components must be coaxially aligned, the spherical fit allows the pivot arm 2 to rotate about the center of the ball without having to be aligned with the axis of the motor 4. As a result, the pivot arm 2 can execute a rotational movement about the motor axis even if it does not run parallel thereto.In this embodiment, each of the first support portion 11 and the second support portion 22 may be made of metal or resin. These components are not substantially compressed during operation, but are subject to only a slight increase in friction. The friction between two smooth surfaces is minimal and does not significantly increase the load on the motor 4.Embodiment 3Referring to FIG. 10.The pivot arm 2 is divided along its longitudinal direction into three sections in the following order: a first rigid section 23, an elastic section 24 and a second rigid section 25.When both the first rigid portion 23 and the second rigid portion 25 are subjected to a force exceeding a predetermined resistance, the elastic portion 24 deforms.The structure of the present application allows the massager to operate without excessive friction between the support body 26 and the flexible layer, which would otherwise result in overloading of the motor 4-a major reason for the shortened life of massagers with this type of motion. Comparable causes for overloading the motor 4 also exist in such devices. In particular, the end of the massage head does not rotate about its own axis, but about the axis of the motor 4, as a result of which a rotational path with a significantly larger radius than that of the massage head is produced.From the perspective of the drive shaft of the motor 4, the larger the radius of rotation, the greater the resistance when friction is applied, since the lever arm corresponds to the radius of the outer circumference of the web. In a massage head rotating about its own axis, the lever arm corresponds to the radius of the head. In a massage head with conical movement, however, the lever arm corresponds to the radius of the movement path.In general, the radius of the rotational path in a massage device is 2 to 4 times the diameter of the massage head in order to offer the user a clearly perceptible massage experience. As a result, the load acting on the motor 4 increases 2 to 4 times. When the user presses the massage head against the body with a large force, the motor 4 can easily enter an overload state. The extent of the overload depends on the behavior of the user, but a long-term and frequent overload inevitably leads to a shortened life of the motor 4 and thus of the entire massage device.To solve this problem, the swinging arm 2 in the present embodiment includes, as a supporting structural member of the vibrating massage head, a central elastic portion 24. the elastic portion 24 must not be too soft; it must provide sufficient support during the swinging movement of the massage head and must not be deformed significantly under normal conditions. It must effectively transmit the force from the third transmission section 21 to the carrier body 26. The elastic section 24 can consist, for example, of relatively hard rubber, a spring or elastic plastic.In normal operation of the device, the elastic section 24 of the swivel arm 2 does not deform. However, when the massage head encounters a high resistance, such as when pressed strongly against the palm, the resistance counteracts the movement of the mechanism. When this resistance becomes larger than a predetermined threshold value, the elastic portion 24 deforms. the predetermined resistance is defined as that sufficient to cause deformation of the elastic portion 24.In this case, the first rigid portion 23, the support body 26 and the flexible layer remain at rest in contact with the palm. The second transmission portion 32 continues to press the third transmission portion 21 so that the second rigid portion 25 continues to move. In other words, the deformation of the elastic portion 24 allows the second rigid portion 25 (and the third transmission portion 21) to move independently of the first rigid portion 23, thereby yielding to the movement of the second transmission portion 32. This prevents the load on the motor 4 from rising in an uncontrolled manner, which prevents overloading of the motor and extends the service life of the massage device.Embodiment 4Referring to Fig. 9.In the support element 1, a first guide bore 13 is provided, the axis of which runs parallel to the axis of the output shaft of the motor 4.The first mounting plate 33 is circular, and the axis of the first transmission portion 31 is coaxially aligned with the first mounting plate 33.The first mounting plate 33 is disposed inside the first guide bore 13.The support element 1 has the first guide bore 13 (the second mounting plate 12 may be part of the support element 1, and the first guide bore 13 may be formed within the second mounting plate 12, still being considered part of the support element 1). The first guide bore 13 is placed over the first mounting plate 33. The first mounting plate 33 is formed as a circular plate, and the first transmitting portion 31 is disposed on the first mounting plate 33. It can be seen that the diameter of the first mounting plate 33 should be greater than the diameter of the movement path of the second transmission section 32.The first mounting plate 33 is arranged completely within the first guide bore 13. The force application point of the first transmission portion 31 and the connection point of the second transmission portion 32 are located at opposite ends of the first guide bore 13, and before deformation may occur at the connection point, the fit between the first mounting plate 33 and the first guide bore 13 must first be released. However, the distance from the force application point of the first transmission portion 31 to the first guide bore 13 is clearly smaller than the distance from the force application point of the first transmission portion 31 to the connection point of the second transmission portion 32 (i.e., the effective length of the second transmission portion 32 is shorter).Therefore, the connection structure at the position of the first guide hole 13 is more resistant to deformation than the connection between the output shaft of the motor 4 and the second transmission portion 32. Originally, the resistance to deformation was determined by the length of the second transmission portion 32 at the connection point (simply speaking, at the point where the output shaft of the motor 4 is inserted into the second transmission portion 32, the tip of the output shaft abuts against the hole wall as a fulcrum, and the edge of the hole abuts against the side wall of the output shaft of the motor 4, which constitutes the point of application of the resistance lever).In the current configuration, the position of the pivot point is displaced closer to the point of force application and further away from the point of application of the resistance lever. Thereby, the transmission member 3 can rotate more effectively about the output shaft of the motor 4.0082] Embodiment 5Referring to FIGS. 2 and 9.The second support portion 22 is detachably connected to the swing arm 2.The second support portion 22 is formed as an annular structure, the outer peripheral wall surface is formed to be spherical and the inner peripheral wall surface is formed to be cylindrical.The second support portion 22 and the swing arm 2 are provided as separate members. Since a spherical fit is formed between the first support portion 11 and the second support portion 22, the centers of the two balls must match. For spherical structures, it is apparent that the maximum cross-sectional diameter lies in the plane passing through the sphere center point. The ball center of the first support portion 11 is located at the center of the depth of the hole structure, which means that the diameters at the both ends of the bore are smaller than the diameter at the center depth. Therefore, it is difficult for the second support portion 22 to pass its ball center cross section through the opening of the first support portion 11.In order to solve this problem, the second support portion 22 is configured as a separate annular member in the present embodiment. Since the ring structure receives no internal support from the swivel arm 2, it is more easily deformable. The second support portion 22 may be disposed across the first support portion 11. When the ring structure is compressed, it may deform into an elliptical shape. The minor half axis of the resulting ellipse is shorter than the original ring diameter, facilitating insertion into the first support portion 11. After the insertion, the second support portion 22 can freely rotate about the ball center. In this state, the swing arm 2 is inserted into the inner ring surface of the second support portion 22.A circular inner ring surface is most suitable because a circular shape under pressure provides a more uniform radial stress distribution. In a square geometry, however, stress concentration occurs at the corners and the diagonal represents the greatest length, making the outer wall thinnest in this direction and thus more susceptible to deformation and breakage.The swing arm 2 is provided with a restricting portion 27 protruding in the circumferential direction. The swing arm 2 is guided by the inner ring of the second support portion 22, the second support portion 22 being positioned between the restriction portion 27 and the support point.In addition, the first support section 11 can also be designed as a separate component. During product assembly, the first support portion 11 and the second support portion 22 are first assembled together before the swing arm 2 and the support member 1 are joined together.In addition, the rear end face of the support member 1 is configured as a second mounting plate 12 which is detachably and fixedly connected to the main body of the support member 1.When assembling the entire conical rotation mechanism, a first assembly is first assembled in which the first support portion 11 and the second support portion 22 are coupled to each other. Subsequently, the swing arm 2 is inserted into the second support portion 22, and the support member 1 is fitted over the first support portion 11.At the same time, a second unit is assembled by connecting the transmission member 3 to the second mounting plate 12, and then the first transmission portion 31 is connected to the output shaft of the motor 4.Finally, the first and second assemblies are assembled to complete the assembly.

Claims

A swing drive mechanism for a massage apparatus, comprising: a support member, a swing arm, a transmission member, and a motor; wherein the support member is connected to a first support portion, the first support portion is connected to and supports the swing arm so as to form a plurality of support points, the plurality of support points being arranged in a circular arrangement about a rotation axis of the motor, and the swing arm is rotatable about the center of the plurality of support points in an arbitrary direction; wherein the transmission member comprises a first transmission portion and a second transmission portion; wherein the first transmission portion is connected to an output shaft of the motor so that the transmission member rotates with the output shaft of the motor; wherein the second transmission portion abuts the swing arm and drives it in a rotation direction of the motor; further, the second transmission portion rotates relative to the swing arm; Further, an abutting position between the second transmission portion and the swing arm is configured such that a longitudinal direction of the swing arm maintains a fixed inclusion angle with the output shaft of the motor.The swing drive mechanism for a massage device according to claim 1, wherein a central portion of the swing arm radially protrudes along its longitudinal direction and forms a second support portion whose wall surface is spherical; wherein the first support portion comprises a spherical hole structure whose wall surface is spherical and whose axis is coaxial with the rotation axis of the motor; wherein a spherical center of the second support portion is on the axis of the first support portion.The swing drive mechanism for a massage device according to claim 1, wherein the first support portion is made of flexible material and connected to a peripheral wall surface of the swing arm; wherein the first support portion forcibly deforms the swing arm to provide space for movement thereof.The swing drive mechanism for a massage device according to claim 1, wherein the first support portion is configured as a plate structure having a circular hole penetrating the plate, an axis of the circular hole being coaxial with the output shaft of the motor; the swing arm being formed cylindrically in the vicinity of the circular hole; wherein L 1 ≤ 3 * L 2 applies; wherein L1 is a maximum circumferential gap between the circular hole and the cylindrical structure; and L2 is a depth of the circular hole.The swing drive mechanism for a massage device according to claim 1, wherein the swing arm is divided into three sections along its longitudinal direction: a first rigid section, an elastic section and a second rigid section, which remain linearly aligned with the elastic section unloaded; wherein the elastic section deforms when a force exceeding a predetermined resistance acts on the first and second rigid sections, whereby the swing arm can flex.The swing drive mechanism for a massager according to claim 1, wherein a third transmission portion is provided at an end of the swing arm, and the second transmission portion applies a force in a rotational direction of the motor to the third transmission portion; further, the second transmission portion applies a force in a direction perpendicular to and away from the rotational axis of the motor to the third transmission portion.The swing drive mechanism for a massage device according to claim 6, wherein the transmission member further comprises a first mounting plate fixedly connecting the first transmission portion and the second transmission portion to each other.The swing drive mechanism for a massager according to claim 7, wherein the third transmission portion is formed as a circular hole extending from the end of the swing arm in the longitudinal direction thereof; the second transmission portion is formed as a shaft structure protruding from the first mounting plate, an axis of the second transmission portion is not coaxial with the rotation axis of the motor; the second transmission portion is inserted into the third transmission portion and abuts against the peripheral wall surface thereof such that the longitudinal direction of the swing arm is not parallel to the output shaft of the motor.The swing drive mechanism for a massage device according to claim 7, wherein the third transmission portion is formed as a cylindrical body extending from the end of the swing arm in the longitudinal direction thereof; the second transmission portion is formed as a circular recess in the first mounting plate, an axis of the second transmission portion being parallel but not coaxial with the rotation axis of the motor; the third transmission portion being disposed at an inclined angle within the second transmission portion relative to the axis thereof.The swing driving mechanism for a massager according to claim 6, wherein the second transmission portion is configured as a slit structure; the slit structure has at least two wall surfaces forming an opening in a direction away from the rotation axis of the motor; the third transmission portion is configured as a cylindrical body extending from the end of the swing arm in the longitudinal direction thereof; the third transmission portion is disposed at the opening of the slit structure; and the wall surface of the slit structure drives the third transmission portion to rotate about the rotation axis of the motor such that the longitudinal direction of the swing arm is not parallel to the output shaft of the motor.

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