KR20020043710A - Torsion damper for vehicles - Google Patents
Torsion damper for vehicles Download PDFInfo
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- KR20020043710A KR20020043710A KR1020000072790A KR20000072790A KR20020043710A KR 20020043710 A KR20020043710 A KR 20020043710A KR 1020000072790 A KR1020000072790 A KR 1020000072790A KR 20000072790 A KR20000072790 A KR 20000072790A KR 20020043710 A KR20020043710 A KR 20020043710A
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- South Korea
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- mass
- drive plate
- rotational force
- dual
- torsional vibration
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/30—Flywheels
- F16F15/315—Flywheels characterised by their supporting arrangement, e.g. mountings, cages, securing inertia member to shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/1215—Leaf springs, e.g. radially extending
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/1232—Wound springs characterised by the spring mounting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
- F16F15/1336—Leaf springs, e.g. radially extending
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
- F16F15/134—Wound springs
- F16F15/1343—Wound springs characterised by the spring mounting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2238/00—Type of springs or dampers
- F16F2238/02—Springs
- F16F2238/026—Springs wound- or coil-like
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
본 발명은 내연기관의 크랭크축에서 발생되는 비틀림 진동을 흡수하기 위하여 설치되는 듀얼매스 플라이휠에 관한 것으로, 좀더 상세하게는 듀얼매스 플라이휠의 비틀림 진동감쇠장치에 관한 것이다.The present invention relates to a dual mass flywheel installed to absorb torsional vibration generated in the crankshaft of an internal combustion engine, and more particularly, to a torsional vibration damping device of a dual mass flywheel.
일반적으로 내연기관의 크랭크축은 주기적으로 회전력이 작용하게 되므로 비틀림 진동이 생기고 있으며, 이러한 비틀림 진동은 차량에 있어서 크랭크축의 회전수가 커지게 됨에 따라 차체의 고유진동과 공진을 일으키게 되고 특히 격심한 진동이 되면 승차감을 나쁘게 할 뿐 아니라 타이밍 기어나 크랭크축을 파손시키는 원인이 되고 있다.In general, the crankshaft of the internal combustion engine generates a torsional vibration because the rotational force is periodically applied, and this torsional vibration causes the natural vibration and resonance of the vehicle body as the number of revolutions of the crankshaft increases in the vehicle, Not only does it worsen the ride, but it also causes damage to the timing gear and the crankshaft.
차량에 있어 크랭크축에서 발생되는 비틀림 진동을 감쇠시키는 장치로서 플라이휠에 토셔널 바이브레이션 댐퍼(torsional vibration damper)라는 진동감쇠장치를 크랭크축 전단의 크랭크 풀리와 일체로 조합시켜서 설치하는 것과, 플라이휠을 두개의 질량으로 분할 구성한 듀얼매스 플라이휠이 있다.As a device for damping the torsional vibration generated by the crankshaft in a vehicle, a vibration damping device called a torsional vibration damper is installed on the flywheel in combination with the crank pulley at the front of the crankshaft, There is a dual mass flywheel divided by mass.
상기한 듀얼매스 플라이휠의 구조는 플라이휠의 질량을 1차질량과 2차질량으로 나누어 구성하고, 상기 2차질량이 다이나믹 댐퍼의 역활을 수행하게 하여 구동계의 진동을 저감시키는 구조이며, 상기 1차질량과 2차질량은 스프링으로 연결되는 구조로 구성되어 있으며, 2차질량에는 클러치가 압착되는 구조로 되어 있다.The dual mass flywheel has a structure in which the mass of the flywheel is divided into a primary mass and a secondary mass, and the secondary mass acts as a dynamic damper to reduce vibration of the drive system. The secondary mass has a structure that is connected by a spring, and the secondary mass has a structure where the clutch is pressed.
차량에 있어서의 듀얼매스 플라이휠은 1차질량은 크랭크축에 고정되어 있으며, 2차질량과 트랜스미션의 입력축이 클러치를 통해 단속되도록 구성되며, 상기 1차질량과 2차질량은 코일스프링의 작동에 의해 진동감소역활을 수행하게 된다.The dual mass flywheel in the vehicle has a primary mass fixed to the crankshaft, and the secondary mass and the input shaft of the transmission are intermittent through the clutch, and the primary mass and the secondary mass are driven by the operation of the coil spring. Vibration reduction role.
종래 기술에서의 1차질량과 2차질량을 연결시키는 코일스프링은 도 6 내지 도 9에 도시된 바와 같이 코일스프링(100)을 원주방향으로 두개 배열한 것과, 반경방향으로 다수 배열한 것과, 원주방향으로 다수 배열한 것 등이 있다.Coil springs connecting the primary mass and the secondary mass in the prior art are two coil springs 100 arranged in the circumferential direction, as shown in Figs. And many arranged in the direction.
그러나 상기와 같은 종래 기술은 엔진의 구동으로 크랭크축의 회전하게 되며, 이에 따라 크랭축에 고정되어 있는 1차질량도 함께 회전하게 되는데, 이때 1차질량의 회전토오크의 변동에 관계없이 1차질량에 설치된 코일스프링(100)이 압출되면서 2차질량에 회전력을 전달시키는 구조로 되어 있기 때문에 크랭크축의 토오크 변동이 작은 저 요동각시에도 코일스프링(100)이 2차질량에 회전력을 전달시키는 상태가 되므로 저 요동각시의 비틀림 진동이 2차질량과 트랜스미션에 전달되는 현상이 나타나게 되어 효율적인 비틀림 진동의 감소효과를 기대하기 어렵다는 것이 단점으로 지적되고 있다.However, the prior art as described above rotates the crankshaft by the driving of the engine, and accordingly rotates the primary mass fixed to the crankshaft, regardless of the variation of the rotational torque of the primary mass. Since the installed coil spring 100 is extruded, the rotational force is transmitted to the secondary mass. Therefore, even when the torque fluctuation of the crankshaft is small, the coil spring 100 transmits the rotational force to the secondary mass. It is pointed out that it is difficult to expect the effect of reducing the torsional vibration effectively because the phenomenon that the torsional vibration at the swing angle is transmitted to the secondary mass and the transmission appears.
본 발명은 상기와 같은 종래 기술에서 나타나는 단점을 해결하고자 창출한 것으로, 듀얼매스 플라이휠의 1차질량과 2차질량을 미동스프링(Slight Shock Spring)과 압축형 코일스프링(Compressive Coil Spring) 두 종류의 스프링으로 연결하는데 상기 미동스프링은 크랭크축의 토오크 변동이 작을 때 2차질량에 회전력을 전달하도록 구성하며 상기 압축형 코일스프링은 크랭크축의 토오크 변동이 어느 정도 커졌을 때 2차질량에 회전력을 전달하도록 하는 구성으로 트랜스미션에 전달되는 비틀림 진동을 효율적으로 감소시킬 수 있도록 하는데 목적을 두고 발명한 것이다.The present invention was created to solve the disadvantages of the prior art as described above, the primary mass and the secondary mass of the dual-mass flywheel two types of fine shock spring (Slight Shock Spring) and compression coil spring (Compressive Coil Spring) It is connected by a spring, the fine spring is configured to transmit the rotational force to the secondary mass when the torque fluctuation of the crankshaft is small, and the compression type coil spring is configured to transmit the rotational force to the secondary mass when the torque fluctuation of the crankshaft is somewhat increased. In order to efficiently reduce the torsional vibration transmitted to the transmission is invented for the purpose.
본 발명은 상기와 같은 목적을 달성하기 위한 수단으로서,The present invention as a means for achieving the above object,
크랭크축의 비틀림 진동을 감소시키기 위하여 듀얼매스 플라이휠의 1차질량과 2차질량 사이에 복수의 압축형 코일스프링을 개재하여서 되는 비틀림 감쇠장치에 있어서,In a torsion damping device in which a plurality of compression-type coil springs are interposed between a primary mass and a secondary mass of a dual mass flywheel in order to reduce the torsional vibration of the crankshaft.
상기 1차질량에 일정간격으로 형성된 홈 각각에 직선상으로 삽입되는 압축형 코일스프링의 양단에 체결되는 볼캐스터와;Ball casters fastened to both ends of the compression-type coil springs inserted linearly into the grooves formed at regular intervals on the primary mass;
상기 1차질량과 2차질량 사이에 개재되며, 상기 압축형 코일스프링 각각을 수용하는 공간이 마련된 채 상기 압축형 코일스프링들 사이로 돌출되어 볼캐스터와 접촉하는 돌출부가 형성되어 있는 드라이브 플레이트와;A drive plate interposed between the primary mass and the secondary mass, the protrusion plate protruding between the compression coil springs and contacting the ball caster with a space for accommodating each of the compression coil springs;
상기 2차질량의 내주면에 일정간격으로 돌출되어 상기 드라이브 플레이트에 회전력을 전달하는 다수의 돌부와;A plurality of protrusions protruding at an interval on the inner circumferential surface of the secondary mass to transmit rotational force to the drive plate;
상기 2차질량과 드라이브 플레이트와의 연결을 위하여 상기 드라이브 플레이트에 일정간격으로 형성되며, 상기 2차질량의 각 돌부가 삽입되는 다수의 회전력 전달구멍과; 및A plurality of rotational force transmission holes formed in the drive plate at a predetermined interval to connect the secondary mass with the drive plate and into which each protrusion of the secondary mass is inserted; And
상기 드라이브 플레이트에 형성된 각 회전력 전달구멍에 삽입 설치되어 2차질량의 돌부 각각에 탄력적으로 접촉하는 다수의 미동스프링;A plurality of fine springs inserted into respective rotational force transmission holes formed in the drive plate and elastically contacting each of the secondary mass protrusions;
을 구성하여서 된 것을 특징으로 하는 것이며,It is characterized by consisting of
또한 상기 압축형 코일스프링 각각의 양단에 체결된 볼캐스터의 볼에 접촉하는 상기 드라이브 플레이트의 돌출부의 접촉면을 곡면으로 형성하여 토오크 전달시 상기 압축형 코일스프링의 축중심을 향해 힘이 전달되게 한 것을 특징으로 하는 것이며,In addition, to form a contact surface of the protrusion of the drive plate in contact with the ball of the ball caster fastened to each end of each of the compression type coil springs to transmit force toward the axis center of the compression type coil springs during torque transmission It is characterized by
또한 상기 드라이브 플레이트에 형성된 다수의 연결구멍 각각에 한쌍씩 개입되는 미동스프링은 압축형 코일스프링의 강성보다 약한 저강성 탄성재질로 된 코일스프링임을 특징으로 하는 것이며,In addition, the fine spring is a pair of each of the plurality of connecting holes formed in the drive plate is characterized in that the coil spring made of a low rigidity elastic material weaker than the rigidity of the compression type coil spring,
또한 상기 미동스프링은 회전력 전달구멍에 삽입되는 돌부를 감싸는 유선형의 판스프링임을 특징으로 하는 것이다.In addition, the fine spring is characterized in that the streamline plate spring surrounding the protrusion inserted into the rotational force transmission hole.
도 1은 본 발명의 듀얼매스 플라이휠의 2차질량을 일부 절개한 정면도.1 is a front view partially cut in the secondary mass of the dual-mass flywheel of the present invention.
도 2는 도 1의 A-A선 단면도.2 is a cross-sectional view taken along the line A-A of FIG.
도 3은 도 2의 B-B선 단면도로서, 본 발명의 요부인 비틀림 진동감쇠장치의3 is a cross-sectional view taken along the line B-B of Figure 2, the main part of the torsional vibration damping device of the present invention;
조립상태를 나타낸 도면.Drawing showing the state of assembly.
도 4는 본 발명의 일요부인 미동스프링의 일부 발췌 확대도.Figure 4 is an enlarged view of a part of the fine spring of the present invention.
도 5는 본 발명의 일요부인 미동스프링의 다른 실시예.5 is another embodiment of fine spring which is an essential part of the present invention.
도 6은 본 발명의 토오크와 종래 기술의 토오크의 비교 곡선도.6 is a comparison curve diagram of the torque of the present invention and the torque of the prior art.
도 7 내지 도 9는 종래 기술의 튜얼매스 플라이휠의 비틀림 진동감쇠장치를7 to 9 is a torsional vibration damping device of the conventional mass-mass flywheel
보인 단면도.Section shown.
※ 도면의 주요부분에 대한 부호의 설명※ Explanation of code for main part of drawing
1 : 듀얼매스 플라이휠 1a : 1차질량1: Dual mass flywheel 1a: 1st mass
1b : 2차질량 2 : 볼캐스터1b: secondary mass 2: ball caster
3 : 압축형 코일스프링 4 : 드라이브 플레이트3: compression coil spring 4: drive plate
5 : 미동스프링 5a : 코일스프링5: Fine spring 5a: Coil spring
5b : 판스프링 12 : 홈5b: leaf spring 12: groove
13 : 돌부 21 : 볼13: protrusion 21: ball
41 : 공간 42 : 돌출부41: space 42: protrusion
43 : 접촉면 44 : 회전력 전달구멍43: contact surface 44: rotational force transmission hole
본 발명의 실시예를 첨부한 도면에 따라서 상세히 설명하면 다음과 같다.An embodiment of the present invention will be described in detail with reference to the accompanying drawings.
도 1은 본 발명의 듀얼매스 플라이휠의 2차질량을 일부 절개한 정면도이며, 도 2는 도 1의 A-A선 단면도이고, 도 3은 도 2의 B-B선 단면도이며, 도 4는 본 발명의 일요부인 미동스프링의 일부 발췌 확대도이고, 도 5는 본 발명의 일요부인 미동스프링의 다른 실시예이며, 도 6은 본 발명의 토오크와 종래 기술의 토오크의 비교 곡선도를 도시한 것으로,1 is a front view partially cut in the secondary mass of the dual mass flywheel of the present invention, Figure 2 is a cross-sectional view taken along the line AA of Figure 1, Figure 3 is a cross-sectional view taken along the line BB of Figure 2, Figure 4 is a main part of the present invention 5 is an enlarged view of a partial excerpt of a fine spring, and FIG. 5 is another embodiment of a fine spring, which is an essential part of the present invention, and FIG. 6 shows a comparison curve of the torque of the present invention and the torque of the related art.
도면부호 1은 듀얼매스 플라이휠을 나타내는 것으로, 상기 듀얼매스 플라이휠(1)은 크랭크축에 연결되는 1차질량(1a)과 트랜스미션에 연결되는 2차질량(1b)으로 나누어진 채 볼베어링(11)에 의하여 회전가능하게 지지되어 있고, 상기 1차질량(1a)에는 일정간격으로 다수 형성된 직선형의 홈(12) 각각에는 볼캐스터(2)가 양단에 체결된 다수의 압축형 코일스프링(3)이 직선상으로 삽입되어 있으며, 상기 1차질량(1a) 내측에는 압축형 코일스프링(3)을 덮어주는 커버가 형성되어 있다.Reference numeral 1 denotes a dual mass flywheel, wherein the dual mass flywheel 1 is divided into a primary mass 1a connected to the crankshaft and a secondary mass 1b connected to the transmission to the ball bearing 11. It is rotatably supported by a plurality of linear grooves 12 formed at a predetermined interval on the primary mass (1a), each of the plurality of compression type coil spring (3) in which a ball caster 2 is fastened to both ends is a straight line The cover is inserted into the cover and covers the compression coil spring 3 inside the primary mass 1a.
상기 1차질량(1a)과 2차질량(1b) 사이에는 드라이브 플레이트(4)가 개입되어 있으며, 상기 드라이브 플레이트(4)의 외주면에는 압축형 코일스프링(3)을 수용하는 공간(41)을 형성시키면서 상기 압축형 코일스프링(3) 양단에 체결된 볼캐스터(2)와 접촉하도록 돌출된 다수의 돌출부(42)가 형성되어 잇다.A drive plate 4 is interposed between the primary mass 1a and the secondary mass 1b, and a space 41 for accommodating the compressed coil spring 3 is provided on the outer circumferential surface of the drive plate 4. While forming, a plurality of protrusions 42 protruding to contact the ball casters 2 fastened to both ends of the compression coil spring 3 are formed.
상기 돌출부(42) 각각의 양측면 즉, 볼캐스터(2)의 볼(21)과 접촉하는 양쪽의 접촉면(43)은 토오크 전달시 항시 압축형 코일스프링(3)의 축중심방향으로 힘을 전달할 수 있도록 곡면으로 형성되어 있다.Both sides of each of the protrusions 42, that is, both contact surfaces 43 contacting the balls 21 of the ball caster 2, may always transmit force in the axial center direction of the compression type coil spring 3 when torque is transmitted. So that it is curved.
또한 상기 드라이브 플레이트(4)의 각 돌출부(42) 내경측으로는 일정간격을 유지한 채 동심원상으로 다수 형성되는 회전력 전달구멍(44)이 형성되어 있는데, 상기 회전력 전달구멍(44) 각각의 중앙으로는 상기 2차질량(1b) 내면에 일정간격으로 돌출된 다수의 돌부(13)들이 하나씩 삽입되어 있다.In addition, a plurality of rotational force transmission holes 44 are formed in the inner diameter side of each of the protrusions 42 of the drive plate 4 while maintaining a constant interval, and are formed in the center of each of the rotational force transmission holes 44. The plurality of protrusions 13 protruding at regular intervals are inserted one by one on the inner surface of the secondary mass 1b.
상기 드라이브 플레이트(4)에 형성된 다수의 회전력 전달구멍(44)에는 다수쌍의 미동스프링(5)이 개입되는데, 상기 미동스프링(5)은 각 회전력 전달구멍(44)의 중앙으로 삽입된 돌부(13)를 기준하여 회전력 전달구멍(44) 각각의 양측에 한쌍씩 삽입되어 돌부(13)를 탄력적으로 지지하는 코일스프링(5a)으로 구성하거나 또는 상기 돌부(13)를 탄력적으로 감싼 채 회전력 전달구멍(44) 내측에 삽입되는 유선형의 판스프링(5b)으로 구성할 수 있다.A plurality of pairs of fine movement springs 5 are introduced into the plurality of rotational force transmission holes 44 formed in the drive plate 4, and the fine movement springs 5 are protrusions inserted into the centers of the respective rotational force transmission holes 44. 13, a pair of coil springs 5a inserted into both sides of each of the rotational force transmission holes 44 to elastically support the protrusions 13, or the rotational force transmission holes with the protrusions 13 elastically wrapped. (44) It can be comprised by the streamlined leaf spring 5b inserted inward.
한편, 본 발명에서 상세하게 도시되지 않았지만 상기 1차질량(1a)의 바깥면은 볼트 장착구멍(14)을 통해 크랭크축과 볼트로서 연결되며, 상기 2차질량(1b)의 바깥면은 클러치 장착구멍(15)에 의하여 클러치와 연결되도록 구성되어 있으며, 또한 상기 1차질량과 2차질량의 중심부에는 허브 플레이트가 장착되고 또 니들베어링은 허브 플레이트의 안쪽으로 압입되어 트랜스미션(도시 없음)의 인풋기어의 지지대 역활을 하도록 구성되어 있다.On the other hand, although not shown in detail in the present invention, the outer surface of the primary mass (1a) is connected as a crankshaft and a bolt through the bolt mounting hole 14, the outer surface of the secondary mass (1b) is clutch mounted It is configured to be connected to the clutch by the hole 15, and the hub plate is mounted at the center of the primary mass and the secondary mass, and the needle bearing is pressed into the hub plate to input the gear of the transmission (not shown). It is configured to serve as a support for the.
이와 같이 구성된 본 발명의 작용을 설명하면 다음과 같다.Referring to the operation of the present invention configured as described above is as follows.
엔진의 구동으로 크랭크축이 회전하게 되면 1차질량(1a)과 2차질량(1b) 그리고 드라이브 플레이트(4)에 회전력이 전달되므로 듀얼매스 플라이휠(1)이 회전운동을 하게 된다.When the crankshaft is rotated by the driving of the engine, since the rotational force is transmitted to the primary mass 1a, the secondary mass 1b, and the drive plate 4, the dual mass flywheel 1 rotates.
상기와 같이 듀얼매스 플라이휠(1)이 크랭크축으로부터 회전운동을 전달받는 과정을 살펴보면, 크랭크축의 회전력은 먼저 크랭크축에 볼트로서 연결된 1차질량(1a)에 전달되고, 이어서 상기 1차질량(1a)에 형성된 각 홈(12)에 삽입 설치된 압축형 코일스프링(3)의 일단 즉, 1차질량(1a)이 회전하는 방향의 선단측에 체결된 볼캐스터(2)에 의하여 드라이브 플레이트(4)에 전달되며, 상기 드라이브 플레이트(4)는 다시 회전력 전달구멍(44)에 삽입되어 있는 돌부(13)를 통하여 2차질량(1b)으로 전달되는 것이며, 이와 같이 회전력이 전달되는 과정에서 듀얼매스 플라이휠(1)에는 비틀림 진동도 함께 전달되는데, 본 발명에서는 듀얼매스 플라휠(1)에 전달되는 비틀림 진동을 효율적으로 감쇠시킬 수 있는 작용을 나타내는 특징을가지고 있다.Looking at the process in which the dual mass flywheel 1 receives the rotational movement from the crankshaft as described above, the rotational force of the crankshaft is first transmitted to the primary mass (1a) connected as a bolt to the crankshaft, and then the primary mass (1a) Drive plate (4) by a ball caster (2) fastened to one end of the compression-type coil spring (3) inserted into each groove (12) formed at the bottom, i.e., the tip side in the direction in which the primary mass (1a) rotates. The drive plate 4 is transmitted to the secondary mass 1b through the protrusion 13 inserted into the rotational force transmission hole 44, and the dual mass flywheel is in the process of transmitting the rotational force. (1) is also transmitted to the torsional vibration, in the present invention has a feature that exhibits an action that can effectively attenuate the torsional vibration transmitted to the dual mass flywheel (1).
즉, 크랭크축의 토오크 변동이 작을 때에는 1차질량(1a)의 회전력이 2차질량(1b)에 전달되는 과정에서는 압축형 코일스프링(3)이 압축변동을 하지 않은 상태에서 드라이브 플레이트(4)의 돌출부(42)에 회전력을 전달하는 상태가 되므로서 상기 드라이브 플레이트(4)에 일정간격으로 형성된 다수의 회전력 전달구멍(44) 각각에 삽입 설치된 미동스프링(5)이 돌부(13)를 탄력적으로 압축되면서 회전력을 2차질량(1b)에 전달하는 상태가 되는데, 상기 미동스프링(5)은 압축형 코일스프링(3)에 비하여 강성이 작은 저강성 재질로 구성되어 있으므로 토오크의 변동이 작은 상태에서 발생되는 비틀림 진동은 상기 미동스프링(5)이 흡수하는 상태가 되므로 비틀림 진동을 효과적으로 감쇠시킬 수 있는 것이며, 크랭크축의 토오크 변동이 커져 요동각이 더 이상 변하지 않는 시점에 도달하기 전 상태(도 6 참조)로서 토오크 변동이 어느 정도 클 때에는 상기한 미동스프링(5)은 탄력적으로 압축되어 더 이상으로 압축될 수 없는 상태가 되며 이때에는 압축형 코일스프링(3)이 탄력적으로 압축되면서 상기 드라이브 플레이트(4)에 회전력을 전달하면서 비틀림 진동을 흡수하게 되 것이다.That is, when the torque fluctuation of the crankshaft is small, in the process of transmitting the rotational force of the primary mass 1a to the secondary mass 1b, the compression type coil spring 3 of the drive plate 4 is not compressed. Since the rotational force is transmitted to the protrusions 42, the fine springs 5 inserted into each of the plurality of rotational force transmission holes 44 formed at predetermined intervals in the drive plate 4 are elastically compressed with the protrusions 13. While the rotational force is transmitted to the secondary mass (1b), the fine spring (5) is made of a low rigidity material with a small rigidity as compared to the compression type coil spring (3) occurs in a small torque fluctuation state The torsional vibration is a state that is absorbed by the fine spring (5) can effectively attenuate the torsional vibration, the torque fluctuation of the crankshaft is increased, the oscillation angle is no longer changed When the torque fluctuation is somewhat large as the state before reaching the viewpoint (see FIG. 6), the fine motion spring 5 is elastically compressed and cannot be compressed any more. In this case, the compression type coil spring 3 This elastic compression will absorb the torsional vibration while transmitting a rotational force to the drive plate (4).
상기에서 미동스프링(5)은 그 축중심방향이 돌부(13)에 대하여 드라이브 플레이트(4)의 회전방향과 일치하도록 설치되어 있으므로 비틀림 진동을 안정적으로 흡수하는 작용을 나타내며, 또한 토오크 변동이 어느 정도 클 때 압축형 코일스프링(3)을 탄력적으로 압축하는 드라이브 플레이트(4)의 돌출부(41)의 접촉면(43)은 상기 압축형 코일스프링(3)이 탄력적으로 압축됨에 따라 볼캐스터(2)의 볼(21)이이동하게 되더라도 압축형 코일스프링(3)의 축중심방향으로 힘을 전달할 수 있는 곡면으로 형성되어 있으므로 비틀림 진동을 안정적으로 흡수하는 작용을 나타내는 것이다.In the above, the fine motion spring 5 is installed so that its axial center direction coincides with the rotational direction of the drive plate 4 with respect to the protrusion 13, thereby stably absorbing the torsional vibration, and the torque fluctuation is somewhat reduced. The contact surface 43 of the protrusion 41 of the drive plate 4 which elastically compresses the compression type coil spring 3 when it is large is the ball caster 2 of the ball caster 2 as the compression type coil spring 3 is elastically compressed. Even though the ball 21 is moved, it is formed as a curved surface capable of transmitting a force in the axial center direction of the compression-type coil spring 3, thereby stably absorbing torsional vibrations.
상기와 같이 크랭크축의 토오크 변동이 작을 때에는 미동스프링(5)의 탄력작용으로 비틀림 진동이 감쇠되고 토오크 변동이 어느 정도 커지는 상태가 되면 압축형 코일스프링(3)의 탄력작용으로 비틀림 진동이 감쇠되므로서 크랭크축에서 발생되는 비틀림 진동을 보다 효율적으로 감쇠시킬 수 있는 것이며, 이와 같은 진동감쇠작용은 크랭크축의 토오크가 반대방향으로 작용할 때에도 똑같은 작용으로 비틀림 진동을 흡수하게 되는 것이다.As described above, when the torque fluctuation of the crankshaft is small, the torsional vibration is attenuated by the resilient action of the fine motion spring (5), and the torsional vibration is attenuated by the elasticity of the compression type coil spring (3) The torsional vibration generated in the crankshaft can be more effectively attenuated. Such vibration attenuation is to absorb the torsional vibration by the same action even when the torque of the crankshaft acts in the opposite direction.
상기와 같은 본 발명에 의하면 듀얼매스 플라이휠의 1차질량과 2차질량 사이에 개입되는 드라이브 플레이트의 돌출부 사이에는 압축형 코일스프링을 탄력설치하고 상기 드라이브 플레이트에 동심원상으로 다수 형성된 회전력 전달구멍에는 다수의 미동스프링을 탄력설치하는 수단으로 크랭크축의 토오크 변동이 작을 때에는 미동스프링이 비틀림 진동을 감쇠시키는 작용을 하도록 하고 크랭크축의 토오크 변동이 클 때에는 압축형 코일스프링이 비트림 진동을 감쇠시키는 작용을 하도록 하므로서 크래크축에서 발생되는 비틀림 진동을 효율적으로 감쇠시키는 효과가 있으며, 이에 다라 차량의 래틀소음 등 트랜스미션에서 발생되는 진동소음이 저감되는 효과를 가져다주며, 또한 미동스프링은 토오크의 변동이 작을 때 작용하는 저강성 탄성재질로 구성하여 요동각이 작을 때 비틀림 진동을 효율적으로 저감시킬 수 있는 효과를 가져다주어 승차감을 좋게 하며 크랭크축이나 타이밍 기어 등 부품의 수명을 연장시키는 이점을 제공하는 유용한 발명인 것이다.According to the present invention as described above, the compression type coil spring is elastically installed between the protrusions of the drive plate interposed between the primary mass and the secondary mass of the dual-mass flywheel, and a plurality of concentric circles on the drive plate are formed in a plurality of rotational force transmission holes. As a means to elastically install the fine spring of the crankshaft, when the torque fluctuation of the crankshaft is small, the fine spring acts to attenuate the torsional vibration. It effectively reduces the torsional vibration generated in the crack shaft, and thus the vibration noise generated in the transmission such as the rattle noise of the vehicle is reduced. Also, the fine spring is operated when the torque fluctuation is small. Rigid elastic material When the smaller the swinging property of each given brings an effect that can be efficiently reduced by the torsional vibration, and improve riding comfort it is useful inventions to provide the advantage of extending the life of components such as the crankshaft or the timing gears.
Claims (4)
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| KR1020000072790A KR20020043710A (en) | 2000-12-04 | 2000-12-04 | Torsion damper for vehicles |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20020058811A (en) * | 2000-12-30 | 2002-07-12 | 이계안 | Dual mass vibration damping flywheel for vehicles |
| KR100478674B1 (en) * | 2001-11-14 | 2005-03-23 | 주식회사 동아오토모티브 | Dual mass vibration damping flywheel for vehicles |
| US20140157945A1 (en) * | 2012-12-10 | 2014-06-12 | Hyundai Motor Company | Dual mass flywheel |
| CN112709782A (en) * | 2019-10-24 | 2021-04-27 | 舍弗勒技术股份两合公司 | Vehicle damper and vehicle |
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|---|---|---|---|---|
| JPS59110456U (en) * | 1983-01-18 | 1984-07-25 | トヨタ自動車株式会社 | Torque fluctuation absorption flywheel |
| JPS6430945A (en) * | 1987-07-11 | 1989-02-01 | Daimler Benz Ag | Split flywheel |
| EP0420830A1 (en) * | 1989-09-20 | 1991-04-03 | Ab Volvo | Flywheel for an internal combustion engine |
| JPH10325446A (en) * | 1997-01-31 | 1998-12-08 | Rohs Voigt Patentverwertungs Gmbh | Twist vibration damping device |
| KR200206541Y1 (en) * | 2000-05-23 | 2000-12-01 | 동아산업주식회사 | Dual mass vibration damping flywheel for vehicles |
-
2000
- 2000-12-04 KR KR1020000072790A patent/KR20020043710A/en not_active Application Discontinuation
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59110456U (en) * | 1983-01-18 | 1984-07-25 | トヨタ自動車株式会社 | Torque fluctuation absorption flywheel |
| JPS6430945A (en) * | 1987-07-11 | 1989-02-01 | Daimler Benz Ag | Split flywheel |
| EP0420830A1 (en) * | 1989-09-20 | 1991-04-03 | Ab Volvo | Flywheel for an internal combustion engine |
| JPH10325446A (en) * | 1997-01-31 | 1998-12-08 | Rohs Voigt Patentverwertungs Gmbh | Twist vibration damping device |
| KR200206541Y1 (en) * | 2000-05-23 | 2000-12-01 | 동아산업주식회사 | Dual mass vibration damping flywheel for vehicles |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20020058811A (en) * | 2000-12-30 | 2002-07-12 | 이계안 | Dual mass vibration damping flywheel for vehicles |
| KR100478674B1 (en) * | 2001-11-14 | 2005-03-23 | 주식회사 동아오토모티브 | Dual mass vibration damping flywheel for vehicles |
| US20140157945A1 (en) * | 2012-12-10 | 2014-06-12 | Hyundai Motor Company | Dual mass flywheel |
| CN112709782A (en) * | 2019-10-24 | 2021-04-27 | 舍弗勒技术股份两合公司 | Vehicle damper and vehicle |
| CN112709782B (en) * | 2019-10-24 | 2024-02-02 | 舍弗勒技术股份两合公司 | Shock absorber for vehicle and vehicle |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A201 | Request for examination | ||
| E902 | Notification of reason for refusal | ||
| E601 | Decision to refuse application |