A vibration damping spring device

Abstract

This invention provides a vibration damping spring device, comprising a mandrel, a housing sleeved outside the mandrel, and a deformation unit filled between the mandrel and the housing. The mandrel includes a base portion and at least one adjusting portion aligned with and spaced apart from the base portion. The deformation unit includes a circumferential deformation portion disposed around the mandrel and a lateral deformation portion filled between the base portion and the adjusting portion. This allows the lateral stiffness of the vibration damping spring device to be adjusted independently of its axial stiffness. In this way, the technical problem in the prior art where the axial and lateral stiffnesses of vibration damping springs correspond to each other and cannot be adjusted independently is solved.

Description

Technical Field

[0001] This invention belongs to the field of vibration damping springs, and particularly relates to a vibration damping spring device. Background Technology

[0002] Vibration damping springs are widely used in industrial production, including rubber springs for vibration isolation platforms in industrial equipment, rubber springs for the primary suspension of subway car bogies, and rubber springs for brake skids in high-speed maglev suspensions. In existing technology, commonly used vibration damping springs mainly include shear type, compression type, and compression-shear type. During use, these vibration damping springs all deform through the deformation of the rubber layer, thereby buffering the force transmitted to the object being damped.

[0003] Figure 1 The diagram schematically illustrates the structure of a shear-type damping spring. For example... Figure 1 As shown, the shear-type damping spring includes an integrally formed spindle 102, a housing 103 surrounding the spindle 102, and a rubber layer 101 filled between the spindle 102 and the housing 103. The base of the spindle 102 is connected to a fixed end, while the housing 103 is connected to the object to be damped. This shear-type damping spring has relatively low vertical stiffness but high horizontal stiffness. In contrast, compression-type damping springs (not shown) have high vertical stiffness but low horizontal stiffness.

[0004] Figure 2 The diagram schematically illustrates the structure of a compression-shear type damping spring. For example... Figure 2 As shown, the compression-shear type damping spring similarly includes an integrally formed spindle 112, a housing 113 surrounding the outside of the spindle 112, and a rubber layer 111 inclined between the spindle 112 and the housing 113. Because the rubber layer 111 is inclined, it has both a certain vertical stiffness and a certain horizontal stiffness.

[0005] However, regardless of the type of damping spring mentioned above, the relationship between its vertical stiffness and horizontal stiffness is one of mutual matching. That is, if the vertical stiffness of any damping spring is adjusted, its horizontal stiffness will also change accordingly, and vice versa. Thus, in many applications, it is impossible to adjust the vertical or horizontal stiffness individually to meet specific needs. Consequently, these existing damping springs cannot meet the requirements of specific applications in an economically viable manner. Summary of the Invention

[0006] To overcome at least one or more of the aforementioned defects in the prior art, a first aspect of the present invention provides a vibration damping spring device, comprising a mandrel, a housing sleeved outside the mandrel, and a deformation unit filled between the mandrel and the housing.

[0007] The mandrel includes a base portion and at least one adjusting portion aligned with and spaced apart from the base portion.

[0008] The deformation unit includes a circumferential deformation portion arranged around the mandrel, and a lateral deformation portion filled between the base portion and the adjustment portion, thereby enabling the lateral stiffness of the damping spring device to be adjusted independently of the axial stiffness of the damping spring device.

[0009] In one embodiment, the thickness of the lateral deformation portion is greater than 50% of the horizontal variable of the damping spring device, but less than 200% of the horizontal variable of the damping spring device.

[0010] In one embodiment, the thickness of the lateral deformation portion is constant, or the thickness is designed to vary along the surfaces opposite the adjustment portion and the base portion.

[0011] In one embodiment, the distance from the centerline of the lateral deformation portion to the free end of the base portion is one-third to two-thirds of the total length of the mandrel.

[0012] In one embodiment, the mandrel includes a plurality of adjustment portions that are axially aligned and spaced apart from each other, and the deformation unit further includes a plurality of additional lateral deformation portions that fill the spaces between the plurality of adjustment portions.

[0013] In one embodiment, at least one of the base portion and the adjustment portion is configured to be hollow.

[0014] In one embodiment, the housing is configured to be open at at least one end and is fitted onto the mandrel, wherein the housing, the mandrel, and the circumferentially deformable portion together form a deformable cavity.

[0015] In one embodiment, the circumferentially deformable portion extends only along a portion of the axial length of the base portion and the adjusting portion.

[0016] According to a second aspect of the invention, a method is provided for adjusting the lateral stiffness of a damping spring device independently of the axial stiffness of the damping spring device, the damping spring device being based on the damping spring device described above.

[0017] In one embodiment, the lateral stiffness of the damping spring device is adjusted by changing the distance from the centerline of the lateral deformation portion of the damping spring device to the free end of the base portion, while ensuring that the axial stiffness of the damping spring device remains essentially unchanged.

[0018] Overall, compared with the prior art, the above-conceived technical solution through the invention can achieve at least the following beneficial effects:

[0019] 1. The vibration damping spring device of the present invention designs the mandrel as a separate unit, comprising a base portion and an adjustment portion, and provides a circumferential deformation portion surrounding the outer side of the mandrel and a lateral deformation portion filling the space between the base portion and the adjustment portion, thereby enabling the lateral stiffness of the vibration damping spring device to be adjusted independently of its axial stiffness. In this way, the technical problem in the prior art where the axial and lateral stiffnesses of vibration damping springs correspond to each other and cannot be adjusted independently is solved.

[0020] 2. According to the present invention, the lateral stiffness of the damping spring device can be adjusted by changing the axial distance from the centerline of the lateral deformation portion to the free end of the base portion, while ensuring that the axial stiffness of the damping spring device remains essentially unchanged. In this way, the lateral stiffness of the damping spring device can be easily adjusted while ensuring that the axial stiffness remains essentially unchanged. Attached Figure Description

[0021] The embodiments of the present invention will now be described in detail with reference to the accompanying drawings, in which:

[0022] Figure 1 The schematic diagram shows the overall structure of a shear-type damping spring according to the prior art;

[0023] Figure 2 The schematic diagram illustrates the overall structure of a compression-shear damping spring according to the prior art;

[0024] Figure 3 The schematic diagram shows the overall structure of a first embodiment of the damping spring device according to the present invention;

[0025] Figure 4 The schematic diagram shows the overall structure of a second embodiment of the damping spring device according to the present invention;

[0026] Figure 5 The schematic diagram illustrates the overall structure of a third embodiment of the damping spring device according to the present invention;

[0027] Figure 6 The schematic diagram illustrates the overall structure of a fourth embodiment of the damping spring device according to the present invention;

[0028] Figure 7 The schematic diagram illustrates the overall structure of a fifth embodiment of the damping spring device according to the present invention;

[0029] Figure 8 The diagram schematically illustrates the axial load-displacement relationship of a compression-shear type damping spring, a shear type damping spring, and a damping spring device according to the present invention.

[0030] Figure 9The diagram schematically illustrates a line graph showing the lateral load-displacement relationship of a compression-shear type damping spring, a shear type damping spring, and a damping spring device according to the present invention.

[0031] Figure 10 The diagram schematically illustrates the axial load-displacement relationship at different distances between the centerline of the lateral deformation section and the free end of the base section of the damping spring device according to the present invention.

[0032] Figure 11 The diagram schematically illustrates the lateral load-displacement relationship between the centerline of the lateral deformation portion and the free end of the base portion of the vibration damping spring device according to the present invention at different distances.

[0033] It should be noted that the accompanying drawings are not necessarily drawn to scale.

[0034] In all the accompanying drawings, the same reference numerals denote the same technical features, specifically: 100-damping spring device; 101-rubber layer; 102-spindle; 103-outer shell; 111-rubber layer; 112-spindle; 113-outer shell; 1-deformation unit; 11-lateral deformation part; 12-circumferential deformation part; 13-deformation cavity; 2-spindle; 21-adjustment part; 22-base part; 3-shell. Detailed Implementation

[0035] To better understand the purpose, structure, and function of this invention, a vibration damping spring device of this invention will be described in further detail below with reference to the accompanying drawings.

[0036] For convenience, the direction extending along the mandrel will be referred to as "axial direction", "vertical direction" or similar terms, the direction perpendicular to the "axial direction" will be referred to as "lateral direction", "horizontal direction" or similar terms, and the direction moving towards the base in the "axial direction" will be referred to as "axial downward" or similar terms.

[0037] According to one embodiment of the present invention, such as Figure 3 As shown, the damping spring device 100 includes a spindle 2, which is configured to stably support any shape of the outer housing 3. In this embodiment, the spindle 2 is configured as a circular cylindrical structure. However, the spindle 2 can also be configured as a square, rectangular, triangular, or other shapes. The housing 3 is fitted over the outer side of the spindle 2 and directly contacts the object to be damped (not shown in the figure), serving to withstand the force applied by the object. The damping spring device 100 also includes a deformation unit 1 filled between the spindle 2 and the housing 3. The deformation unit 1 supports the housing 3, thereby transmitting the force on the housing 3 to the deformation unit 1, thus achieving buffering through the deformation of the deformation unit 1.

[0038] In one embodiment, such as Figure 3As shown, the mandrel 2 includes a base portion 22 for connection to a fixed end (foundation or similar, not shown). The mandrel 2 also includes adjusting portions 21 aligned with and spaced apart from the base portion 22. The number of adjusting portions 21 can be arbitrary along the axial direction of the base portion 22, and deformation units 1 are filled between the base portion 22 and the adjusting portions 21, as well as in the intervals between the adjusting portions 21. In other words, the mandrel 2 is manufactured as a split structure. In this way, each adjusting portion 21 and each deformation unit 1 constitutes a vibration damping unit. Therefore, by providing multiple adjusting portions 21 and deformation units 1 filled between them, multiple vibration damping units can be constructed to provide multi-directional and multi-layered vibration damping for the object to be damped.

[0039] In this configuration, multiple damping units arranged along the axial direction of the base portion 22 can be constructed into a damping spring device 100 with an overall shape resembling bamboo. Each damping unit corresponds to a bamboo joint. Thus, the present invention provides a bamboo-joint type damping spring device. In this embodiment, only one damping unit is provided. Specifically, an adjustment portion 21 is provided along the axial direction of the base portion 22. However, as mentioned above, multiple adjustment portions 21 are also feasible.

[0040] In one embodiment, such as Figure 3 As shown, the deformation unit 1 includes a circumferential deformation portion 12 disposed between the mandrel 2 and the housing 3. The inner wall of the circumferential deformation portion 12 is adapted to the shape of the outer wall of the mandrel 2 and is fitted against the outer wall of the mandrel 2, while the outer wall of the circumferential deformation portion 12 is fitted against the inner wall of the housing 3. When the housing 3 is subjected to an axially downward force, the circumferential deformation portion 12 deforms, buffering the axially downward force.

[0041] like Figure 3 As shown, the deformation unit 1 further includes a lateral deformation portion 11 filled between the base portion 22 and the adjustment portion 21. Preferably, the lateral deformation portion 11 is integrally formed with the circumferential deformation portion 12. In this way, the deformation unit 1 can support the housing 3 in both the lateral and axial directions. When the housing 3 is subjected to a lateral force, the lateral deformation portion 11 deforms, buffering the lateral force.

[0042] With the above structure, the lateral stiffness of the damping spring device 100 can be adjusted independently of the axial stiffness of the damping spring device.

[0043] Figure 8 The diagram schematically illustrates the axial load-displacement relationship of a compression-shear type damping spring, a shear type damping spring according to the prior art, and a damping spring device according to the present invention. Figure 8As shown, the three axial load-displacement relationship curves basically coincide, that is, with the structure of the present invention, the axial stiffness of the damping spring device is approximately the same as that of the compression-shear type damping spring and the shear type damping spring. Figure 9 The diagram schematically illustrates the lateral load-displacement relationship of a compression-shear type damping spring, a shear type damping spring according to the prior art, and a damping spring device according to the present invention. Figure 9 As shown, the three axial load-displacement relationship curves are all different from each other. That is, using the structure of the present invention, the lateral stiffness of the damping spring device is significantly different from that of the compression-shear type damping spring and the shear type damping spring. In other words, by using the above structure, the damping spring device 100 according to the present invention can obtain significantly different lateral stiffness while maintaining stable axial stiffness; that is, the lateral stiffness of the damping spring device 100 can be adjusted independently of the axial stiffness of the damping spring device. Therefore, it can be well adapted to the requirements of lateral stiffness and axial stiffness in different applications.

[0044] In one embodiment, the thickness of the lateral deformation portion 11 is set to be greater than 50% of the horizontal variable of the damping spring device, but less than 200% of the horizontal variable of the damping spring device.

[0045] Furthermore, according to the present invention, by adjusting the axial position of the lateral deformation portion 11, the lateral stiffness can be adjusted while maintaining a substantially constant axial stiffness. Specifically, in one embodiment of the present invention, such as Figure 3 As shown, the distance from the centerline of the lateral deformation section 11 to the free end of the base section 22 can be set to one-third to two-thirds of the total length of the mandrel 2. By changing the position of the lateral deformation section 11 in the axial direction of the mandrel 2, the lateral stiffness of the damping spring device 100 can be changed while maintaining the same axial stiffness.

[0046] To address this, axial and lateral loads were applied to the mandrel 2 at three different locations where the lateral deformation portion 11 was positioned, respectively, to measure its axial and lateral stiffness. These positions, located near the free end of the base portion 22, are designated as the first, second, and third positions. The first position is one-third of the total length of the mandrel 2 from the free end of the base portion 22; the second position is half the total length of the mandrel 2 from the free end of the base portion 22; and the third position is two-thirds of the total length of the mandrel 2 from the free end of the base portion 22. The results are shown in [the table / document / etc.]. Figure 10 and 11 middle.

[0047] like Figure 10As shown, regardless of whether the lateral deformation part 11 is located at the first, second, or third position on the spindle 2, the damping spring device 100 will experience the same axial displacement under the same axial load. That is, regardless of the position of the lateral deformation part 11 on the spindle 2, the axial stiffness of the damping spring device 100 remains essentially constant. And as... Figure 11 As shown, when the lateral deformation part 11 is positioned at different first, second, or third positions on the spindle 2, the damping spring device 100 will undergo different lateral displacements under the same lateral load. In other words, the lateral stiffness of the damping spring device 100 will change as the lateral deformation part 11 is positioned at different positions on the spindle 2.

[0048] Therefore, according to the present invention, by adjusting the different axial positions of the transverse deformation part 11 on the mandrel, the transverse stiffness of the device can be adjusted without changing the axial stiffness of the entire device. This adjustment method is very convenient to implement and achieves good results.

[0049] In one embodiment of the present invention, such as Figure 3 As shown, the upper and lower surfaces of the lateral deformation portion 11 are parallel and located on different horizontal planes. Specifically, the thickness of the lateral deformation portion 11 remains constant. However, according to the present invention, the thickness of the lateral deformation portion 11 can also be variable. Figure 6 As shown, the thickness of the transversely deformable portion 11 is set to gradually decrease from both ends towards the center. Figure 7 As shown, the transverse deformation section 11 is designed in a wavy shape, causing its thickness to vary accordingly. This non-constant thickness transverse deformation section further enhances the adjustability of the transverse stiffness.

[0050] exist Figure 3 In the illustrated embodiment, the housing 3 is configured with at least one open end and is fitted onto the mandrel 2. In the illustrated embodiment, the housing 3 is configured with one open end and the other closed end. It is readily understood that in an embodiment not shown, the housing 3 may also be configured with both ends open. In this way, as... Figure 3 As shown, a deformation cavity 13 is formed between the housing 3, the spindle 2, and the circumferential deformation section 12. In this configuration, the housing 3 and the deformation cavity 13 together form a deformation region, providing a deformation distance for the circumferential deformation section 12 and further buffering the forces acting on the housing 3.

[0051] In this way, when the housing 3 is subjected to an axially downward force, the housing 3 moves downward, generating a downward force on the circumferential deformation part 12, causing the circumferential deformation part 12 to elastically deform downward, thereby buffering the axial force on the housing 3. When the axially downward force disappears, the circumferential deformation part 12 returns to its initial deformation position after elastic deformation. During the downward movement of the housing 3, since the housing 3, the spindle 2, and the circumferential deformation part 12 together form a deformation cavity 13, the housing 3 moves within the deformation cavity 13, thereby buffering the force it receives. This configuration provides a deformation distance for the circumferential deformation part 12 and a displacement distance for the housing 3 to buffer the force, further improving the buffering effect.

[0052] Simultaneously, one side of the circumferential deformation section 12 is in contact with the outer surface of the mandrel 2, and the other side is in contact with the inner surface of the housing 3. In this way, when the housing 3 is subjected to a lateral force, the housing 3 is in contact with the circumferential deformation section 12, resulting in a large contact area and stable force transmission. Therefore, the housing 3 can continuously and stably transmit the applied force to the deformation unit 1. At this time, the lateral deformation section 11 undergoes elastic deformation, buffering the force applied to the housing 3. When the lateral force disappears, the lateral deformation section 11 recovers its elastic deformation and returns to its initial deformation position.

[0053] Figure 4 The specific structure of a second embodiment of the vibration damping spring device 100 of the present invention is shown. This embodiment differs from the first embodiment in that it employs a different circumferential deformation portion 12. In this embodiment, a transverse deformation portion 11 is formed between the base portion 22 and the adjustment portion 21, but the height of the circumferential deformation portion 12 is less than the length of the spindle 2, and it only extends partially around the spindle 2.

[0054] Figure 5 The specific structure of a third embodiment of the vibration damping spring device 100 of the present invention is shown. This embodiment differs from the first embodiment in that it employs a different circumferential deformation portion 12. In this embodiment, a transverse deformation portion 11 is formed between the base portion 22 and the adjusting portion 21, but the height of the circumferential deformation portion 12 is less than the length of the spindle 2, and it only extends partially around the spindle 2. In particular, the circumferential deformation portion 12 is arranged perpendicular to the housing 3.

[0055] According to a preferred embodiment of the present invention, the mandrel 2 may further consist of a base portion 22 and a plurality of adjusting portions 21. The plurality of adjusting portions 21 are aligned axially with the base portion 22, and are spaced apart from each other. The spaces between each adjusting portion 21 are filled with additional lateral deformation portions 11. The vibration damping spring device 100 configured in this way can buffer lateral forces at multiple angles and levels, improving the applicability of the vibration damping spring device 100.

[0056] According to a preferred embodiment of the present invention, at least one of the base portion 22 and the adjusting portion 21 of the mandrel 2 may be configured as a hollow structure. In this way, the weight of the damping spring device 100 can be reduced without changing the axial stiffness and transverse stiffness of the damping spring device 100.

[0057] The operation of the damping spring device 100 according to the present invention is as follows.

[0058] First, the damping spring device 100 is placed between the fixed end (foundation or similar, not shown in the figure) and the object to be damped (not shown in the figure).

[0059] When the object to be damped applies an axial downward force to the damping spring device 100, the object first transmits the force to the housing 3. The housing 3 is driven by the force to move the adjusting part 21 downward, and the circumferential deformation part 12 deforms to buffer the axial force applied to the object to be damped.

[0060] When the object to be damped applies a lateral force to the damping spring device 100, the object first transmits the force to the housing 3. The housing 3 is driven by the force to move the adjusting part 21 laterally, and the lateral deformation part 11 deforms to buffer the lateral force applied to the object to be damped.

[0061] When the external force disappears, the circumferential deformation part 12 or the lateral deformation part 11 recovers its deformation, completing the buffering work of the object to be damped.

[0062] When it is necessary to adjust the lateral stiffness separately while keeping the axial stiffness constant, this can be achieved by changing the axial distance between the lateral deformation part 11 and the free end of the base part 22.

[0063] It is understood that the present invention has been described through some embodiments, and those skilled in the art will recognize that various changes or equivalent substitutions can be made to these features and embodiments without departing from the spirit and scope of the invention. Furthermore, under the teachings of the present invention, these features and embodiments can be modified to adapt to specific situations and materials without departing from the spirit and scope of the invention. Therefore, the present invention is not limited to the specific embodiments disclosed herein, and all embodiments falling within the scope of the claims of this application are within the protection scope of the present invention.

Claims

1. A vibration damping spring device, characterized by It includes a mandrel (2), a housing (3) sleeved on the outside of the mandrel (2), and a deformation unit (1) filled between the mandrel (2) and the housing (3). The mandrel (2) includes a base portion (22) and a plurality of adjustment portions (21) aligned with and spaced apart from the base portion (22). The plurality of adjustment portions (21) are arranged sequentially, aligned axially and spaced apart from each other. The deformation unit (1) includes a circumferential deformation portion (12) arranged around the mandrel (2) and a lateral deformation portion (11) filled between the base portion (22) and the adjustment portion (21). The deformation unit (1) also includes a plurality of additional lateral deformation portions (11) filled between the plurality of adjustment portions (21). The lateral deformation portions are configured to buffer lateral forces and allow the lateral stiffness of the damping spring device to be adjusted independently of the axial stiffness of the damping spring device. The housing (3) is configured to be open at least one end and is fitted onto the mandrel (2). The housing (3), the mandrel (2), and the circumferential deformation portion (12) together form a deformation cavity (13).

2. The vibration damping spring device according to claim 1, characterized by The thickness of the lateral deformation portion (11) is greater than 50% of the horizontal variable of the damping spring device, but less than 200% of the horizontal variable of the damping spring device.

3. The vibration damping spring device according to claim 2, characterized in that, The thickness of the lateral deformation portion (11) is constant, or the thickness is designed to vary along the surfaces opposite to the adjustment portion (21) and the base portion (22).

4. The damping spring device according to any one of claims 1 to 3, characterized in that, The distance from the centerline of the transverse deformation portion (11) to the free end of the base portion (22) is one-third to two-thirds of the total length of the mandrel.

5. The damping spring device according to any one of claims 1 to 3, characterized in that, At least one of the base portion (22) and the adjustment portion (21) is constructed to be hollow.

6. The damping spring device according to any one of claims 1 to 3, characterized in that, The circumferential deformation portion (12) extends only along a portion of the axial length of the base portion (22) and the adjustment portion (21).

7. A method for adjusting the lateral stiffness of a vibration damping spring device independently of its axial stiffness, characterized in that, The damping spring device is the damping spring device according to any one of claims 1 to 6.

8. The method according to claim 7, characterized in that, The lateral stiffness of the damping spring device is adjusted by changing the distance from the center line of the lateral deformation section to the free end of the base section, while ensuring that the axial stiffness of the damping spring device remains basically unchanged.

Images