Compression-type mass damper and suspension system and vehicle using it

Abstract

Compression type mass damper (1), comprising: a damping mass (10) formed with an open space, wherein the damping mass (10) surrounds an outer surface of a target through the open space and absorbs vibration of the target, a weight body (50) surrounded by the damping mass (10), the weight body applying weight to the damping mass (10), and a compression plate (60) surrounded by the damping mass (10), the compression plate (60) exerting a fixing force on the open space, characterized in that a damper pin (70) passes through the damping mass and is attached to the compression plate (60) to prevent separation of the weight body (50).

Description

Background(a) Technical area

[0001] The present invention relates to a mass damper which reduces a resonance phenomenon of a vehicle, and more particularly to a compression-type mass damper which is fixed (eg, press-fitted) to an outer surface of a target (eg, target object) in a press-fitting manner (eg, press-fitting manner), and a suspension system and a vehicle using the same. (b) Description of the prior art

[0002] In general, NVH (noise, vibration, harshness) of vehicles are factors that must be reduced to meet legal regulations, such as the following European regulations (with specified decibel levels): EU#1(92dB), EU#9(81dB) and EU#6(78dB).

[0003] As an example of efforts to reduce NVH, there is a method in which a mass damper formed by coupling a mass of rubber or urethane with a bracket is connected to a drive system, a vehicle body joint part, or an exhaust system (e.g., exhaust system).

[0004] For example, in a method of connecting the mass damper to a drive system, the mass damper is attached to an axle housing so that the magnitude of vibration of the axle can be reduced by vibration absorption by the mass damper. In a method of connecting the mass damper to the vehicle body joint, the mass damper is attached to the joint between a chassis and a vehicle body so that the magnitude of vibration of the vehicle body can be reduced by vibration absorption by the mass damper. In a method of connecting the mass damper to the exhaust system, the mass damper is attached to an exhaust pipe (e.g., exhaust pipe) so that the magnitude of vibration of the exhaust pipe can be reduced by vibration absorption by the mass damper.

[0005] For example, the use of the mass damper attached to a vibration source or vibration transmission path helps reduce NVH to meet European regulations such as EU#1(92dB), EU#9(81dB) and EU#6(78dB).

[0006] However, NVH is characterized by being aggravated by the resonance phenomenon of a vibration source originating from the road and a vibration source originating from the engine / powertrain system. Specifically, a suspension system is a basic structure connecting the vehicle body to the chassis and acts as a path through which vibration amplified by resonance is transmitted. Therefore, it is difficult to meet European regulations, such as EU#1 (92 dB), EU#9 (81 dB), and EU#6 (78 dB), by using only a mass damper.

[0007] Furthermore, the suspension system applies a bushing similar to the mass damper to adjust the rigidity of the joint between the vehicle body and a suspension component to thereby reduce vibration, but it is ineffective in avoiding the influence of a resonance frequency of vibration transmitted from the road or the influence of a resonance frequency of vibration generated from the engine / drive system and transmitted to the vehicle body.

[0008] From DE 195 37 462 A1 a compression-type mass damper according to the preambles of claims 1, 14, 15 and 16 is known. Explanation of the invention

[0009] The present invention has an object to provide a compression-type mass damper which is coupled to a component of a suspension system in a press-fit manner and which is particularly capable of avoiding, without reducing the rigidity of the suspension system, the influence of a resonance frequency of vibration transmitted from the road and a resonance frequency of vibration generated from an engine / drive system and transmitted to a vehicle body, and is also directed to a suspension system and a vehicle using the same.

[0010] These objects are achieved by a compression-type mass damper according to claim 1, 14, 15 or 16 and by a suspension system according to claim 17 and by a vehicle according to claim 19. Advantageous embodiments are the subject of the dependent claims.

[0011] According to the present invention, there is provided a compression-type mass damper comprising: a damping mass formed with an open space, the damping mass surrounding (e.g., enclosing) an outer surface of a target (e.g., target object) through the open space and absorbing vibration of the target; a weight body (e.g., mass body) surrounded by the damping mass, the weight body applying (e.g., exerting) weight to the damping mass; and a compression plate surrounded by the damping mass, the compression plate applying a fixing force to the open space.

[0012] In a variant of the present invention, a damper pin passes through the damping mass and is attached to the compression plate to prevent separation of the weight body.

[0013] In a further variant of the present invention, the damping mass comprises a compression body having the open space and equipped with the compression plate, the compression body being provided with a plurality of projections, the projections being exposed to the open space and brought into contact with the target.

[0014] In yet another variant of the present invention, the weight body is formed with a mass loading space that can be changed in size and shape to adjust a weight of the weight body.

[0015] In yet another variant of the present invention, the damping mass comprises a compression body having the open space and equipped with the compression plate, wherein the compression plate exerts a force on an outer body of the compression body to exert the fixing force on the open space.

[0016] All variants of the invention mentioned so far can also be combined with each other and all together with regard to their features.

[0017] The damping mass may be made of an elastic material (e.g., a spring-elastic material), and the weight body and the compression plate may be made of metal. The weight body and the compression plate may be formed together with the damping mass by injection molding.

[0018] The damping mass may further comprise: a mass body having the weight body above the open space, and an elastic body (eg, a spring-elastic body) that integrally connects the compression body (eg, one-piece) with the mass body and absorbs the vibration.

[0019] The elastic body may have an inverted trapezoidal cross-section extending from the mass body toward the compression body and formed with a cavity having an inverted trapezoidal cross-section.

[0020] The weight body can have a shape corresponding to a shape of the mass body.

[0021] The compression plate may have a shape corresponding to that of the compression body.

[0022] The damper pin can pass through both a pin passage hole concentric with a pin receiving space of the mass body and a shaft hole of the weight body, and can be attached (e.g., fixed) to (e.g., in) a pin fixing hole of the compression plate. The damper pin can be fixed to the pin fixing hole by a fixing protrusion provided at one end of a pin shaft that passes through the pin passage hole and the shaft hole.

[0023] According to the present invention, there is provided a suspension system comprising: a compression-type mass damper having a damping mass configured to absorb vibration, a weight body applying weight to the damping mass, a compression plate applying a fixing force to an open space of the damping mass, and a damper pin passing through the damping mass and fixed to the compression plate; and a leaf spring to which the compression-type mass damper is fixed such that the leaf spring is surrounded by the compression-type mass damper in a lateral direction of the leaf spring.

[0024] The leaf spring has an eye portion provided with a bushing, and the compression-type mass damper may be attached (e.g., fixed) to a portion of the leaf spring other than the eye portion.

[0025] According to the present invention, a vehicle comprises: a compression-type mass damper having a damping mass configured to absorb vibration, a weight body applying weight to the damping mass, a compression plate applying a fixing force to an open space of the damping mass, and a damper pin passing through the damping mass and fixing the compression plate, and a suspension system having a leaf spring to which the compression-type mass damper is attached (e.g., fixed) such that the compression-type mass damper surrounds (e.g., encloses) an outer surface of the leaf spring, the suspension system being configured to avoid, by using the compression-type mass damper, the influence of a resonance frequency of vibration transmitted from a road and a resonance frequency of vibration generated by an internal combustion engine and a drive system and transmitted to a vehicle body.

[0026] A rear axle configured to transmit power to a wheel attached to the suspension system may include a bolt-type mass damper connected to the rear axle via a bolt (e.g., a screw). The bolt-type mass damper may be configured to absorb vibration of the rear axle.

[0027] In the present invention, a mass damper for reducing vibration is press-fitted and integrally fixed (e.g., fixed) to a component of a suspension system in a press manner, thereby realizing the following advantages and effects.

[0028] First, because the mass damper is directly mounted to the suspension system, it can reliably avoid the influence of a resonance frequency of vibration transmitted from the road and a resonance frequency of vibration generated by an internal combustion engine / powertrain system and transmitted to a vehicle body. Second, the mass damper is attached (or mounted) to the suspension by pressing (or is press-fitted to it), thereby avoiding a problem of load concentration at a bolt-type connecting part (e.g., a screw connecting part) that occurs with a bolt-type mass damper. Third, because a body part of a leaf spring of the suspension system is used, the rigidity of a spring eye connecting the leaf spring to the vehicle body can be maintained.Fourth, the vibration absorption performance of the suspension system can be significantly increased, thereby maximizing the vehicle's ride and handling performance. Fifth, because the suspension system can significantly increase the vehicle's NVH reduction rate, the present invention can meet regulatory requirements such as European regulations EU#1 (92 dB), EU#9 (81 dB), and EU#6 (78 dB). Brief description of the drawings Fig. 1 is a perspective view of a compression-type mass damper according to an embodiment of the present invention. Fig. 2 is an assembly cross section of the compression type mass damper according to the present invention. Fig. 3 is a view illustrating modifications of the compression type mass damper of the present invention. Fig. 4 is a view showing the configuration of a suspension system using the compression type mass damper according to the present invention. Fig. 5 is a view showing a pressing device of a leaf spring and the compression type mass damper according to the present invention. Fig. 6 is a view showing an example of a vehicle having, as a component thereof, the suspension system using the compression type mass damper according to the present invention, which contributes to a reduction of NVH of the vehicle. Description of specific embodiments

[0029] It is to be understood that the term "vehicle" or "vehicular" or other similar term, as used herein, includes motor vehicles in general, such as passenger cars, including sport utility vehicles (SUVs), buses, trucks, various commercial vehicles, watercraft, including a variety of boats and ships, aircraft, and similar vehicles, and also includes hybrid vehicles, electric vehicles, plug-in hybrid electric vehicles, hydrogen-powered vehicles, and other alternative-fuel vehicles (e.g., fuels derived from resources other than petroleum). As referred to herein, a hybrid vehicle is a vehicle that has two or more power sources, e.g., both gasoline-powered and electric-powered vehicles.

[0030] For example, the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the invention. As used herein, the singular forms "a," "an," and "the" are intended to include the plural forms unless the context clearly indicates otherwise. It is further to be understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of the recited features, integers, steps, acts, elements, and / or components, but do not preclude the presence or addition of one or more other features, integers, steps, acts, elements, components, and / or groups thereof. As used herein, the term and / or includes any and all combinations of one or more of the features listed in connection therewith.Throughout the specification, unless explicitly stated otherwise, the word "comprises" and variations thereof, such as "comprising" or "having," are intended to include the recited elements, but not to exclude any other elements. Additionally, the terms "unit," "units," and "modules" described in the specification refer to units for performing at least one function and / or operation, and may be implemented by hardware components or software components, and combinations thereof.

[0031] Furthermore, the control logic of the present invention may be embodied as a non-transitory computer-readable medium on a computer-readable medium containing executable program instructions executeable by a processor, a controller, or the like. Examples of computer-readable media include, but are not limited to, ROM, RAM, compact disc (CD)-ROMs, magnetic tapes, floppy disks, flash drives, smart cards, and optical data storage devices. The computer-readable medium may also be distributed in network-coupled computer systems such that the computer-readable medium is stored and executed in a distributed manner, e.g., through a telematics server or a controller-area network (CAN).

[0032] Fig. 1 and Fig. 2 illustrate a compression type mass damper according to an embodiment of the present invention.

[0033] With reference to Fig. 1, the compression type mass damper 1 includes a damping mass 10 that performs a damping function by absorbing vibration, a weight body 50 that maintains (e.g., forms) an upper shape of the damping mass 10 and applies weight to the damping mass 10, a compression plate 60 that maintains (e.g., forms) a lower shape of the damping mass 10 and applies / exerts a fixing force to the damping mass 10 that is subjected to compression from a target member, and a damper pin 70 that is inserted into the damping mass 10 and fixes the weight body 50 and the compression plate 60 to the damping mass 10.

[0034] With reference to Fig. 2, the damping mass 10 is divided into a mass body 20, which forms an upper portion of the damping mass 10, a compression body 30, which forms a lower portion of the damping mass 10, and an elastic body 40, which forms an intermediate portion of the damping mass 10. The damping mass 10 is made of an elastic material, such as rubber, for elastic compression deformation. Specifically, the damping mass 10 is formed integrally (e.g., one-piece) with the weight body 50 and the compression plate by injection molding.

[0035] In one embodiment, the mass body 20 has, in a central portion thereof, a pin receiving space 20-1 and a pin passing hole 20-2, which are formed concentrically (to each other). The mass body 20 has an at least approximately rectangular (e.g., square) parallelepiped structure with a predetermined thickness and surrounds the damper body (e.g., weight body) 50. Specifically, the pin receiving space 20-1 is formed by removing a central portion of the mass body 20 in a circular shape and is used as a space in which the damper pin 70 is received. The pin passing hole 20-2 passes through a portion of the mass body 20 in which the pin receiving space 20-1 is not formed. The pin passing hole 20-2 is used as a passage through which the damper pin 70 is connected to the compression plate 60.

[0036] In one embodiment, the compression body 30 includes an outer body 33 having a planar shape and is formed integrally (e.g., one-piece) with the mass body 20 through the elastic body 40. The compression body 30 includes an outer body 33 forming an open space for surrounding the target member and applying compression (e.g., pressing force) thereto (e.g., compressing it). An inner body 31 is formed in a central portion of the open space, and the damper pin 70 is disposed on the inner body 31. Specifically, unlike the outer body 33, the inner body 31 protrudes to enter a cavity 40-1, which is an internal space of the elastic body 40, thereby allowing the compression plate 60 to be attached / fixed to the damper pin 70 through the protruding portion of the inner body 31.Further, the inner body 31 has a central hole 31-1 therein so that a portion of the compression plate 60 to which the damper pin 70 is attached can be open through the central hole 31-1. The outer body 33 has protrusions on an inner surface thereof so that when the outer body 33 is pressed onto the target member, the contact force therebetween can be increased. In one embodiment, the protrusions include bottom protrusions 35-1 protruding from a bottom surface of the outer body 33 and side protrusions 35-2 protruding from a side surface of the outer body 33. The bottom protrusions 35-1 and the side protrusions 35-2 are protrusions arranged in a row, and each has a hemispherical, rectangular, trapezoidal, or triangular cross-section.

[0037] In one embodiment, the elastic body 40 integrally connects the mass body 20 to the compression body 30 and has the cavity 40-1, which is a hollow space for facilitating elastic deformation due to a load. Specifically, the elastic body 40 has an inverted trapezoidal cross-section, in which a side thereof adjacent to the mass body 20 is longer than a side thereof adjacent to the compression body 30. Thus, the cavity 40-1 also forms the hollow space having an inverted trapezoidal cross-section.

[0038] With reference to Fig. 2, the weight body 50 is made of metal and has a rectangular (e.g., square) parallelepiped shape with a predetermined thickness. The weight body 50 has, at a central portion thereof, a mass loading space 53 (e.g., mass receiving space) and a shaft hole 55, and is integrally formed with the mass body 20 by injection molding such that the weight body 50 is surrounded by the mass body 20. The mass loading space 53 is formed by removing a central portion of the damper body (e.g., weight body) 50 in a predetermined shape and is provided as a space in which the pin receiving space 20-1 of the damper mass 10 is formed. The shaft hole 55 passes through a portion of the damper body 50 in which the mass loading space 53 is not formed, and is therefore provided as a space in which the pin passing hole 20-2 of the damper mass 10 is formed.The mass cargo space 53 may be modified into one of those as shown in . Fig. 3. As shown in Fig. 3, with respect to the weight body 50, based on the mass loading space 53 formed in a circular shape with a standard diameter D, it can be modified to a large mass loading space 53-1 formed in a square shape with a predetermined side length L, or to a small mass loading space 53-2 formed in a circular shape with a reduced diameter d smaller than the standard diameter D. Therefore, the mass loading space 53 has a volume smaller than that of the large mass loading space 53-1 but larger than that of the small mass loading space 53-2. Thereby, the weight of the weight body 50 can be adjusted.

[0039] With reference to Fig. 2, the compression plate 60 is made of a metal plate and is formed integrally (e.g., one-piece) with the compression body 30 by injection molding such that the compression plate 60 is surrounded by the compression body 30. The compression plate 60 includes a pin fixing body 61, which forms an internal structure to which the damper pin 70 is fixed, and a deformable body 63, which is pressed onto the target member and therefore exerts a fixing force. Specifically, the pin fixing body 61 is fixed to the damper pin 70 through the pin fixing hole 61-1 and is arranged together with the inner body 31 of the compression body 30 in the cavity 40-1, which is the internal space of the elastic body 40.

[0040] With reference to Fig. 2, the damper pin 70 includes a large-diameter flange concentrically provided at a first end of the damper pin 70, and a pin shaft 71 provided at a second end thereof and having a predetermined length with a fixing protrusion 73 (e.g., a fixing boss) protruding from the pin shaft 71. Specifically, the length of the pin shaft 71 is a predetermined length at which, when the damper pin 70 is connected to the damping mass 10, the pin shaft 71 is prevented from protruding from the damping mass 10. Further, the diameter of the fixing protrusion 73 is a diameter sufficient for the fixing protrusion 73 to be forcibly inserted into the pin fixing hole 61-1 of the compression plate 60, so that the force for fastening / fixing the fixing protrusion 73 to the compression plate 60 is formed.A slit is formed in the fixing protrusion 73 to allow the fixing protrusion 73 to be elastically deformed. Therefore, when the elastic body 40 is damaged due to an external impact or malfunction, the damper pin 70 also functions to maintain the connection of the weight body 50 to the compression plate 60, so that the weight body 50 can be fixed in position.

[0041] Fig. 4 illustrates an example of a suspension system to which the compression type mass damper 1 is applied. As in Fig. 4, the suspension system 100 is a suspension system for a commercial vehicle, which is installed adjacent to each of the left and right wheels receiving power from a rear axle 200. The suspension system 100 includes a leaf spring 110 provided with the compression-type mass damper 1. The compression-type mass damper 1 of Fig. 4 is the same as the compression type mass damper 1, which is designed with reference to the Fig. 1 to 3. Therefore, the compression body 30 is pressed onto the leaf spring 110 in such a manner that the compression body 30 surrounds the leaf spring 110 in the lateral direction of the leaf spring 110. Thereby, the fixing force by which the damping mass 10 and the leaf spring 110 are fixed to each other can be increased by the pressing force (or compression force) exerted by the compression plate 60 on the leaf spring 110.

[0042] In particular, the compression between the damping mass 10 and the leaf spring 110 can be realized by a pressing machine. With reference to Fig. 5, the damping mass 10 and the leaf spring 110 are temporarily attached to each other so that the compression body 30 surrounds the leaf spring 110 in the lateral direction. Thereafter, the temporarily assembled intermediate product is placed on its side and then arranged on (e.g., on, e.g., in) a lower mold 300-2 of the pressing machine 300. Subsequently, the upper mold 200-1 is moved onto the lower mold 300-2. Then, the compression body 30 and the compression plate 60 are brought into close contact with the leaf spring 110 in the lateral direction and fixed to each other by the pressing force of the upper and lower molds 200-1 and 300-2. In this case, the lower projections 35-1 and the side projections 5-2 of the compression body 30 are deformed, so that the contact force between the lower body 30 and the leaf spring 110 is increased.Specifically, the lower protrusions 35-1 and the side protrusions 35-2 function to prevent the damping mass 10 from being pushed or removed from the original position thereof even when a displacement of the leaf spring 110 is caused by a load applied thereto when the vehicle is running.

[0043] Fig. 6 is an example of a vehicle 100-1 having, as a component thereof, a suspension system 100 equipped with a compression-type mass damper 1. As in Fig. 6, the vehicle 100-1 includes the suspension system 100 connected to a vehicle body at a position adjacent to each of the left and right wheels, a rear axle 200 transmitting power to the left and right wheels, and an NVH reduction unit including the compression-type mass damper 1, bushings 120-1, 120-2, and 120-3, and a bolt-type mass damper 1-1.

[0044] In one embodiment, the compression-type mass damper 1 surrounds and exerts compression (e.g., compresses) the leaf spring 110 in the lateral direction (e.g., sideways direction) of the leaf spring 110. Therefore, when the suspension system 100 acts as a path through which a resonant frequency of vibration from a road and / or a resonant frequency of vibration from an engine / powertrain system is / are transmitted to the vehicle body after being amplified, the compression-type mass damper 1 prevents the influence of the resonant frequency by the leaf spring 110, thereby significantly mitigating the resonant frequency amplification of the suspension system 100. These results have been confirmed by the result of a practical vehicle test in which noise is reduced by a maximum of 14 dB.

[0045] In one embodiment, the bushings 120-1, 120-2, and 120-3 are installed in an eye portion formed at each of the two ends of the leaf spring 110. The first, second, and third bushings 120-1, 120-2, and 120-3 have different types of structures and shapes, whereby the rigidity of a vehicle body connection part can be changed, so that vibrations can be reduced. In particular, when the first, second, and third bushings 120-1, 120-2, and 120-3 are used together with the compression-type mass damper 1, the connection point between the vehicle body and the eye portion of the leaf spring 110 can be configured so that a change in the rigidity thereof is minimized.

[0046] In one embodiment, the bolt-type mass damper 1 is connected to the rear axle 200 by a bolt (e.g., a screw), whereby a resonance phenomenon of a vibration source by the engine / drive system at the rear axle 200 can be avoided.

[0047] As described above, a compression-type mass damper according to an embodiment of the present invention includes a damping mass 10 that absorbs vibrations, a weight body 50 that exerts weight on the damping mass 10, a compression plate 60 that provides a fixing force in an open space of the damping mass 10, and a damper pin 70 that is fixed to the compression plate 60 through the damping mass 10. The compression-type mass damper 1 is pressed onto an outer surface of a plate spring 110 and fixed in a pressing manner through (e.g., via) the open space of the damping mass 10, and is thereby used as a component of the suspension system 110.The suspension system 100 is applied to a vehicle 100-1 and is capable of avoiding the influence of a resonant frequency of vibration transmitted from a road and a resonant frequency of vibration transmitted from an engine / powertrain system to the vehicle body without reducing the rigidity of the suspension system 100. In particular, the resonant frequency avoidance of the suspension system 100 results in a reduction in NVH, thereby meeting current legal requirements.

[0048] Although the present invention has been described with reference to specific embodiments, it will be apparent to those skilled in the art that various changes and modifications can be made without departing from the scope of the invention as defined in the following claims.

Claims

[1] Compression type mass damper (1), comprising: a damping mass (10) formed with an open space, wherein the damping mass (10) surrounds an outer surface of a target through the open space and absorbs vibration of the target, a weight body (50) surrounded by the damping mass (10), the weight body applying weight to the damping mass (10), and a compression plate (60) surrounded by the damping mass (10), the compression plate (60) exerting a fixing force on the open space, characterized by , that a damper pin (70) passes through the damping mass and is attached to the compression plate (60) to prevent separation of the weight body (50). [2] The compression type mass damper (1) according to claim 1, wherein the damping mass (10) is made of an elastic material, and wherein the weight body (50) and the compression plate (60) are made of metal. [3] Compression type mass damper (1) according to claim 1 or 2, wherein the weight body (50) and the compression plate (60) are formed together with the damping mass (10) by injection molding. [4] Compression type mass damper (1) according to one of claims 1 to 3, wherein the damping mass (10) comprises: a compression body (30) having the open space and equipped with the compression plate (60), a mass body (20) comprising the weight body (50) above the open space, and an elastic body (40) which integrally connects the compression body (30) to the mass body (20) and absorbs the vibration. [5] A compression-type mass damper (1) according to claim 4, wherein the compression body (30) is provided with a plurality of projections (35-1), the projections being exposed to the open space and brought into contact with the target. [6] A compression type mass damper (1) according to claim 5, wherein each of said projections (35-1) has a hemispherical shape. [7] A compression-type mass damper (1) according to any one of the preceding claims in combination with claim 4, wherein the elastic body (40) has an inverted trapezoidal cross-section extending from the mass body (20) toward the compression body (30) and formed with a cavity (40-1). [8] A compression-type mass damper (1) according to claim 7, wherein the cavity (40-1) has an inverted trapezoidal cross section. [9] The compression-type mass damper (1) according to any one of claims 1 to 8, wherein the weight body (50) has a shape corresponding to a shape of the mass body (20) and is formed with a mass loading space (53). [10] A compression-type mass damper (1) according to claim 9, wherein a weight of the weight body (50) is adjusted by changing the size and shape of the mass loading space (53). [11] A compression-type mass damper (1) according to any one of claims 1 to 10, wherein the compression plate (60) has a shape corresponding to that of the compression body (30). [12] The compression-type mass damper (1) according to any one of claims 1 to 11, wherein the damper pin (70) passes through both a pin passing hole (20-2) concentric with a pin receiving space (20-1) of the mass body (20) and a shaft hole (55) of the weight body (50) and is fixed to a pin fixing hole (61-1) of the compression plate (60). [13] A compression-type mass damper (1) according to claim 12, wherein the damper pin (70) is fixed to the pin fixing hole by means of a fixing projection (73) provided at one end of a pin shaft (71) passing through the pin passing hole (20-2) and the shaft hole (55). [14] Compression type mass damper (1), comprising: a damping mass (10) formed with an open space, wherein the damping mass (10) surrounds an outer surface of a target through the open space and absorbs vibration of the target, a weight body (50) surrounded by the damping mass (10), the weight body applying weight to the damping mass (10), and a compression plate (60) surrounded by the damping mass (10), the compression plate (60) exerting a fixing force on the open space, wherein the damping mass (10) comprises a compression body (30) having the open space and being equipped with the compression plate (60), characterized by , that the compression body (30) is provided with a plurality of projections (35-1), the projections being exposed to the open space and brought into contact with the target. [15] Compression type mass damper (1), comprising: a damping mass (10) formed with an open space, wherein the damping mass (10) surrounds an outer surface of a target through the open space and absorbs vibration of the target, a weight body (50) surrounded by the damping mass (10), the weight body applying weight to the damping mass (10), and a compression plate (60) surrounded by the damping mass (10), the compression plate (60) exerting a fixing force on the open space, characterized by , that the weight body (50) is formed with a mass loading space (53) which can be changed in size and shape in order to adjust a weight of the weight body (50). [16] Compression type mass damper (1), comprising: a damping mass (10) formed with an open space, wherein the damping mass (10) surrounds an outer surface of a target through the open space and absorbs vibration of the target, a weight body (50) surrounded by the damping mass (10), the weight body applying weight to the damping mass (10), and a compression plate (60) surrounded by the damping mass (10), the compression plate (60) exerting a fixing force on the open space, wherein the damping mass (10) comprises a compression body (30) having the open space and being equipped with the compression plate (60), characterized by , that the compression plate (60) exerts a force on an outer body (33) of the compression body (30) to exert the fixing force on the open space. [17] Suspension system for a vehicle, comprising: a compression-type mass damper (1) having a damping mass (10) adapted to absorb vibration, a weight body (50) which applies weight to the damping mass (10), a compression plate (60) which applies a fixing force to an open space of the damping mass (10), and a damper pin (70) which passes through the damping mass (10) and is fixed to the compression plate (60), and a leaf spring (110) to which the compression-type mass damper (1) is attached such that the leaf spring (110) is surrounded by the compression-type mass damper (1) in a lateral direction of the leaf spring (110). [18] The suspension system according to claim 17, wherein the leaf spring (110) has an eyelet portion provided with a bushing (120-1), and wherein the compression-type mass damper (1) is fixed to a portion of the leaf spring (110) other than the eyelet portion. [19] Vehicle comprising: a compression-type mass damper (1) having a damping mass (10) adapted to absorb vibration, a weight body (50) applying weight to the damping mass (10), a compression plate (60), which applies a fixing force to an open space of the damping mass (10), and a damper pin (70) which passes through the damping mass and fixes the compression plate (60), and a suspension system having a leaf spring (110) to which the compression-type mass damper is attached such that the compression-type mass damper (1) surrounds an outer surface of the leaf spring, the suspension system being configured to avoid, by using the compression-type mass damper (1), an influence of a resonance frequency of vibration transmitted from a road and a resonance frequency of vibration generated by an internal combustion engine and a drive system and transmitted to a vehicle body. [20] A vehicle according to claim 19, wherein the suspension system is applied to a commercial vehicle. [21] A vehicle according to claim 19 or 20, wherein a rear axle (200) arranged to transmit power to a wheel attached to the suspension system comprises a bolt-type mass damper connected to the rear axle (200) via a bolt, the bolt-type mass damper being arranged to absorb vibration of the rear axle.

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