JP5670676B2 - Damper device - Google Patents

Damper device Download PDF

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Publication number
JP5670676B2
JP5670676B2 JP2010200644A JP2010200644A JP5670676B2 JP 5670676 B2 JP5670676 B2 JP 5670676B2 JP 2010200644 A JP2010200644 A JP 2010200644A JP 2010200644 A JP2010200644 A JP 2010200644A JP 5670676 B2 JP5670676 B2 JP 5670676B2
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damper
spring
annular
input
peripheral
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JP2012057694A (en
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尚久 山下
尚久 山下
田中 克典
克典 田中
山口 誠
誠 山口
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アイシン・エィ・ダブリュ工業株式会社
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/021Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • F16H2045/0231Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284Multiple disk type lock-up clutch

Description

  The present invention relates to a damper device that reduces hysteresis accompanying expansion and contraction of a damper spring.

  As is well known, a torque converter is a type of joint that can transmit engine power to a transmission using a working fluid as a medium. A pump impeller that is turned by the engine and a movement of the working fluid that is sent out by the rotation of the pump impeller. The turbine runner that rotates around the turbine runner, and the stator that changes the direction of the working fluid from the turbine runner and guides it to the pump impeller.

  FIG. 12 shows a conventional torque converter, in which (a) is a pump impeller, (b) is a turbine runner, (c) is a stator, and (d) is a lock-up damper device. (E) is contained within. Therefore, the front cover (f) is rotated by obtaining power from the engine, and the pump impeller (a) integrated with the front cover (f) is rotated. As a result, the turbine runner (robot) is mediated by the working fluid. ) Turns.

  A transmission input shaft (not shown) is fitted to the turbine hub (g) of the turbine runner (b), and the rotation of the turbine runner (b) can be transmitted to the transmission (not shown). Since the torque converter is a kind of fluid coupling, the turbine runner (B) starts to rotate as the rotational speed of the pump impeller (A) increases, and the speed of the turbine runner (B) increases as the speed increases. A) approaches the rotation speed. However, in the torque converter using the working fluid as a medium, the rotational speed of the turbine runner (b) cannot be the same as that of the pump impeller (b).

  Therefore, as shown in the figure, when the lockup damper device (d) is provided and the rotational speed of the turbine runner (b) exceeds a predetermined range, the lockup damper device (d) The piston (H) moves in the axial direction so that the clutch (R) is turned on. Therefore, the clutch plate is sandwiched between the front cover (f) and the clutch receiver (nu) connected so as not to rotate relative to each other via the spline shaft (na), and the lockup damper device (d) is used as the front cover. It can rotate at the same speed as (f).

  Since the lock-up damper device (d) is connected to the turbine hub (g), the turbine hub (g) is directly rotated by the front cover (f), and the power from the engine is transferred to the transmission. It can be transmitted with high efficiency of almost 100% without any loss due to the fluid.

  In this way, when the rotational speed of the turbine runner (B) increases and a certain condition is reached, the piston (H) operates and the clutch (R) is turned ON, and the turbine runner (B) ), But before the clutch (re) is turned on, the rotational speeds of the turbine runner (b) and front cover (f) are not completely the same, so the clutch (re) is turned on. In some cases, an impact torque based on the speed difference between the two is generated.

  Therefore, in order to mitigate the impact torque generated when the clutch (re) is turned on and absorb the torque fluctuation of the engine in the clutch engaged state, the front cover (f) and the turbine runner (b) A lock-up damper device (d) having damper springs (le), (le)... And inner diameter side damper springs (e), (e).

  When the clutch (re) of the lock-up damper device (d) rotating at the same speed as the turbine runner (b) is turned on and the speed is slightly the same as that of the slightly faster front cover (f), the turbine runner (b) ) The torque which tries to turn faster is applied. This shock torque is absorbed and compressed by the damper springs (le), (le)... And the inner diameter side damper springs (e), (e). It is configured.

  Conventionally, the structure of the damper device is known in various ways. However, the “elastic coupling mechanism” disclosed in Japanese Patent Application Laid-Open No. 2002-48218 is an elastic coupling mechanism having a torsion spring, which reduces the sliding resistance between the torsion spring and other members. I try to reduce it. That is, it is a mechanism for transmitting torque and absorbing / damping torsional vibration, and includes a drive plate, a driven plate, a torsion spring, and a spring holder. The torsion spring elastically connects the drive plate and the driven plate in the rotational direction. The spring holder is disposed so as to be rotatable relative to the drive plate and the driven plate. The spring holder includes a cylindrical outer peripheral support portion that supports the outer peripheral side of the torsion spring, a cylindrical inner peripheral support portion that supports the inner peripheral side of the torsion spring, and a connecting portion that connects the two. ing.

The “torque transmission device” according to Japanese Patent Application Laid-Open No. 2002-155959 suppresses the occurrence of wear on the outer peripheral portion of the drive plate by the expansion and contraction operation of the torsion spring and the sliding friction with the drive plate due to the centrifugal force.
Therefore, a plurality of torsion springs that elastically connect the drive plate and the damper hub are provided in the circumferential direction in the space formed between the outer peripheral portions of the drive plate and the sub plate. An annular plate-like annular member that slides and supports the outer peripheral surface of the torsion spring in a line contact state on the inner peripheral surface is provided, and between the outer peripheral surface of the annular member and the cylindrical inner peripheral surface of the drive plate outer peripheral portion. A gap is formed.

Thus, by suppressing the sliding friction accompanying the expansion and contraction of the damper spring, the generation of a large hysteresis torque is prevented, and as a result, the torsional vibration absorbing performance of the damper device is improved and the durability of the damper device is also improved. .
By the way, in the case of the “elastic coupling mechanism” according to Japanese Patent Application Laid-Open No. 2002-48218, a spring holder is provided, and the spring holder is disposed so as to be relatively rotatable with respect to the drive plate and the driven plate and supports the outer peripheral side of the torsion spring. A cylindrical outer peripheral support portion, a cylindrical inner peripheral support portion that supports the inner peripheral side of the torsion spring, and a connecting portion that connects the two. That is, it is configured as an intermediate member with a U-shaped cross section into which the torsion spring fits. However, the durability of the spring holder becomes a problem by rotating with the expansion and contraction of the torsion spring, and the expansion and contraction of the torsion spring is accompanied. Therefore, when the damper device is operated, there is a problem that a resonance point is generated due to the mass of the spring holder.

  In the case of the “torque transmission device” according to Japanese Patent Application Laid-Open No. 2002-155959, an annular plate-like annular member that slides and supports the outer peripheral surface of the torsion spring in a line contact state on the inner peripheral surface is provided. A gap is formed between the outer peripheral surface of the cylinder and the inner peripheral surface of the cylindrical portion of the outer peripheral portion of the drive plate. By arranging the annular plate-like annular member on the outer peripheral side of the torsion spring, there is a problem in terms of space, and there is also a problem of friction caused by sliding between the annular member and the input side member.

  FIG. 13 shows a conventional damper device. That is, this is a damper device constituting the lockup damper device (d) of the torque converter shown in FIG. (W), (W) are input side members, (F), (F) are output side members, (G) is a turbine hub, (L) is a damper spring, (O) is an inner diameter side damper spring. Represents each. The drum part (yo) which comprises a clutch (re) is continued with the input side member (wa), and both input side members (wa) and (wa) are mutually connected via the rivet (ta).

  Therefore, the torque input to the input side member (wa), (wa) is a damper spring via the spring presser (le), (le) formed integrally with the input member (wa), (wa). (L) and the inner diameter side damper spring (e) attached to the output member side is pressed, but the outer diameter side damper spring (le) and the inner diameter side damper spring (e) are ring-shaped intermediate members. (So) are connected in series.

  Therefore, the spring presser (le), the damper spring (le) pressed by the (le) and the inner diameter side damper spring (e) are compressed and deformed to press the output members (f) and (f) to transmit torque. Is done. The ring-shaped intermediate member (sole) in which the damper spring (le) and the inner diameter side damper spring (e) are connected in series is rotatably supported.

  In the conventional damper device shown in FIG. 13, damper springs (le), (le),... Are arranged in a circumferential direction on a predetermined radius, and these damper springs (le), (le),. Is constrained so that it does not come off by an outer peripheral wall (tube) extended by curving one input member (wa) in the outer peripheral direction. Accordingly, when the damper spring (le) is stretched and deformed by being sandwiched between the input members (wa) and (wa) and the intermediate member, the damper spring (le) contacts and rubs against the outer peripheral wall (tu) and the side wall (ra). . In particular, the outer peripheral wall (tsu) is greatly rubbed by the centrifugal force acting on the damper spring (le), so that a large hysteresis is generated and the vibration absorbing ability is impaired.

  FIG. 13B is a schematic diagram showing a case where one damper spring (le) is divided into one coil and rubs against the outer peripheral wall (tu) of the input member (wa). ) Represents the mass of (), (Y) represents the spring constant, and (Z) represents the contact between the coil (ne) and the outer peripheral wall (tu). Therefore, if a force acts on the input member (wa) in the direction of the arrow, the intermediate member (sole) also moves in the direction of the arrow via the damper spring (le). In this case, the amount of movement of the intermediate member (so) is smaller than the amount of movement of the input member (wa), and the difference in the amount of movement becomes the amount of compressive deformation of the damper spring (le), and the pushing force acting on the intermediate member (so) Pressure (impact torque) can be relaxed.

When the damper spring (le) expands and contracts, the coils (ne), (ne), etc. constituting the damper spring (le) are rubbed against the outer peripheral wall (tsu), but the damper spring ( When the number of turns of the coil (ne), (ne),... Is 6, the hysteresis torque generated when the coils (ne), (ne),. If so, the total is 60. That is, each coil (ne), (ne).
"Elastic connection mechanism" according to Japanese Patent Application Laid-Open No. 2002-48218 "Torque transmission device" according to JP-A-2002-155959

  As described above, the lockup damper device incorporated in the conventional torque converter has the above-described problems. The problems to be solved by the present invention are these problems, and provide a more compact damper device that absorbs torsional vibrations by suppressing hysteresis associated with expansion and contraction of a damper spring (torsion spring) as much as possible. Here, the object to which the damper device of the present invention is attached is not limited to the torque converter, but also includes a starting device, an HV damper, and the like.

  The damper device targeted by the present invention includes a damper spring capable of absorbing small vibrations associated with engine torque fluctuations, and is configured to relieve large shock torque when the clutch is turned on. . That is, the basic structure as a damper device is the same as in the past, and a plurality of damper springs are arranged on the outer circumferential side between the input member and the output member, and the damper is operated according to the torque fluctuation acting on the input member. The spring can expand and contract to transmit torque to the output member.

  By the way, in the conventional damper device, the damper springs arranged on the outer periphery are restrained so as not to be detached by the input member or the output member. However, in the present invention, the damper spring is fixed by the annular member separated from the input member or the output member. It is a structure constrained on the radius. Therefore, the annular member is a ring body having an inner peripheral side opened, and the annular member is attached to the outer periphery of the input member or the output member in a rotatable state. The damper spring is accommodated in the ring-shaped space of the annular member. The cross-sectional shape of the annular member generally forms a smooth arc, but the circumference of the arc is not limited. The circumference of the arc restricts only the outer peripheral side of the damper spring, and the outer peripheral side and both sides are constrained. In some cases, the inner diameter side may also be restrained.

  In the damper device according to the present invention, a plurality of damper springs are mounted between the input member and the intermediate member or the output member, and these damper springs are arranged on a constant radius on the outer peripheral side, and are restrained by an annular member having a ring body. It does not come off the damper device. That is, damper springs arranged in a circumferential direction are accommodated in a ring-shaped space having an inner peripheral side opened. Therefore, the damper spring does not come off from the annular member, and fluctuations in the engine torque and a large impact torque input to the input member are absorbed by the damper spring expanding and contracting.

  By the way, the annular member that restrains the damper spring is a component member that is separated from the input member, the intermediate member, or the output member and is not directly involved in torque transmission. The distance of sliding in contact with the inner circumferential surface of the annular member is reduced. As a result, the hysteresis of the damper spring is reduced and the torsional vibration absorbing capacity of the damper device is improved. The annular member is sized to have a ring-like space required to accommodate the damper spring, and a compact damper device is configured. Further, since the annular member does not participate in torque transmission, another resonance point due to the provision of the annular member does not occur.

The damper apparatus which concerns on this invention, the cyclic | annular member of a damper apparatus, and the relationship of a damper spring are shown. The specific example of the torque converter provided with the damper apparatus of this invention. The front view containing the partial cross section of a damper apparatus. The specific example of the annular member which comprises the damper apparatus. The specific example of the torque converter provided with the damper apparatus of this invention. The specific example of the annular member which comprises the damper apparatus. The specific example of the torque converter provided with the damper apparatus of this invention. The Example which shows the damper apparatus which concerns on this invention. The specific example of the torque converter provided with the damper apparatus of this invention. The specific example of the annular member which comprises the damper apparatus. Schematic which shows the damper apparatus of another form which concerns on this invention. The example of the torque converter provided with the conventional damper apparatus. The relationship between the conventional damper apparatus and the input member of a damper apparatus, and a damper spring is shown.

  FIG. 1 shows a damper device according to the present invention, wherein 1a and 1b are input members, 2a and 2b are output members, 3 is a turbine hub, 4 is a damper spring, and 28 is an inner diameter side damper spring. Yes. The drum portion 5 constituting the clutch is continuous with the input member 1 a, and both the input members 1 a and 1 b are connected via a rivet 6. The output members 2a and 2b are sandwiched between the input members 1a and 1b, and a ring-shaped intermediate member 31 having separators 8a and 8b formed on the outer periphery and the inner periphery is interposed between the output members 2a and 2b. .

  Therefore, the torque input to the input members 1a and 1b presses the damper spring 4 via the spring retainers 7a and 7b formed integrally with the input members 1a and 1b, and the compressed damper spring 4 is intermediate. The inner diameter damper spring 28 is compressed via the separators 8a and 8b of the member 31 and the output members 2a and 2b are pressed to transmit torque. That is, the separator 8a formed on the outer periphery is pressed by the outer damper spring 4 and the intermediate member 31 rotates, and as a result, the inner peripheral damper spring 28 is pressed by the inner peripheral separator 8b to thereby output the output members 2a and 2b. Rotating torque is transmitted.

  Here, between the spring retainers 7a and 7b of the input members 1a and 1b and the output member 2, a damper spring 4 is arranged on the outer diameter side, and an inner diameter side damper spring 28 is arranged on the inner diameter side, and the damper spring 4 and the inner diameter side damper are arranged. The intermediate member 31 having the separators 8a and 8b formed between the springs 28 is connected in series. The inner diameter side damper springs 28, 28... Are accommodated in spring accommodating portions 30a, 30b formed in the output members 2a, 2b, and the intermediate member 31 is rotatably supported.

  By the way, in the damper device of the present invention, the damper springs 4, 4... Are arranged in a circumferential direction on a predetermined radius, and these damper springs 4, 4... Are attached to the outer peripheral side of the input members 1a, 1b. An annular member 9 is attached to the outer periphery of the input members 1a and 1b. The annular member 9 forms a ring body, and the inner peripheral side is opened to form a ring-shaped space.

  Although the annular member 9 is attached to the outer periphery of the input members 1a and 1b, it is not connected and can rotate freely independently. That is, it is a component member that is separated from the input members 1a and 1b and does not directly participate in torque transmission. That is, the annular member 9 corresponds to the outer peripheral wall (tsu) shown in FIG. 12, and the damper spring 4 is fitted and restrained in the ring-shaped space of the annular member 9.

  When the damper spring 4 is stretched and deformed by being sandwiched between the spring retainers 7a and 7b of the input members 1a and 1b and the separator 8a of the intermediate member 31, the damper spring 4 contacts and rubs against the annular member 9. Therefore, although hysteresis is generated, it is theoretically about ½ compared to the hysteresis generated between the outer wall and the outer wall of the conventional damper device, and the torsional vibration absorbing ability is improved.

  FIG. 1B is a schematic diagram showing a case where one damper spring 4 rubs against the annular member 9. If a force acts on the input member 1 in the direction of the arrow, the intermediate member 31 is also moved via the damper spring 4. Move in the direction of the arrow. In this case, the amount of movement of the intermediate member 31 is smaller than the amount of movement of the input member 1, and the difference in the amount of movement becomes the amount of compressive deformation of the damper spring 4 to relieve the pressing force (impact torque) acting on the intermediate member 31. I can do it.

  When the damper spring 4 is expanded and contracted, the coils 12, 12... Constituting the damper spring 4 are rubbed against the annular member 9, but the coils 12, 12,. When the number is 6, assuming that the hysteresis of each of the coils 12, 12,. That is, the hysteresis is theoretically about ½ compared to the case of the conventional damper device. The annular member 9 is rotatably supported on the outer periphery of the input member 1, and therefore does not move with the input member 1, and the coils 12, 12. The annular member 9 is merely moved by the friction. Therefore, theoretically, the hysteresis is about ½ of the conventional hysteresis.

  FIG. 2 shows a torque converter provided with the damper device of the present invention. In the figure, 13 is a pump impeller, 14 is a turbine runner, 15 is a stator, 16 is a damper device of the present invention, and 17 is a piston, which are accommodated in a torque converter outer shell 18. The pump impeller 13 rotates with the power from the engine, and the rotation of the pump impeller 13 rotates the turbine runner 14 through the working fluid.

  When the rotational speed of the pump impeller 13 increases and the rotational speed of the turbine runner 14 exceeds a predetermined range, the piston 17 is activated and the clutch 19 is turned on, and the rotational torque of the front cover 20 is reduced to the drum. Is transmitted to the unit 5. That is, a clutch receiver 21 connected to the front cover 20 is attached to the clutch 19, and a clutch hub 22 that is riveted is provided on the clutch receiver 21. .., And the drum side clutch plates 24, 24,... Are sandwiched between the clutch receiver 21 and the torque of the front cover 20 is transmitted to the drum unit 5. The

  Then, the damper spring 4 is pressed from the drum portion 5 via the spring retainers 7a and 7b of the input members 1a and 1b, and the damper spring 4 is compressed and deformed by the pressing force, and passes through the intermediate member 31 and the inner diameter side damper spring 28. It is transmitted to the output members 2a and 2b. The output members 2a and 2b are attached to the turbine hub 3, and the rotational torque of the front cover 20 is transmitted to the turbine hub 3 and is transmitted to a transmission input shaft (not shown) fitted in the shaft hole of the turbine hub 3. .

  By the way, the piston 17 can be operated by sending hydraulic oil to the oil chamber 26 through the oil passage 25, and if the oil pressure in the oil chamber 26 decreases, a coil spring attached between the piston 17 and the clutch receiver 21. The piston 17 is retracted by the spring force of 27 and the clutch 19 is turned off. When the clutch 19 is turned on, there is a speed difference between the turbine runner 14 and the front cover 20, and thus an impact torque is generated. This impact torque is alleviated by the damper device 16.

  Even in the lockup state in which the clutch 19 is turned on, the torque fluctuation of the engine can be absorbed by the damper device 16. As described in FIG. 1 above, damper springs 4, 4... Are attached to the damper device 16, and these damper springs 4, 4. Torque fluctuation can be absorbed. Further, inner diameter side damper springs 28, 28,... Having a large spring constant are attached to the inner diameter side, and the damper spring 4 and the inner diameter side damper spring 28 are formed by an intermediate member 31 having separators 8a, 8b formed on the outer periphery and the inner periphery. They are connected in series.

  At this time, the damper device 16 according to the present invention is provided with an annular member 9 that can restrain the damper spring 4 to be removed so as to reduce hysteresis accompanying expansion and contraction of the damper spring 4 and to prevent the damper spring 4 from coming off. It is attached to the outer periphery. The damper device 16 of the torque converter shown in FIG. 2 is mounted as described in FIG.

  FIG. 3 is a plan view including a cross section of the damper device 16. As shown in the figure, three damper springs 4, 4... Are attached to the outer diameter side, and six inner diameter side damper springs 28, 28. The inner diameter side damper springs 28, 28... Are fitted and attached to spring accommodating portions 30a, 30b formed on the output members 2a, 2b, and the intermediate member 31 is freely rotatable between the output members 2a, 2b. It is interposed in a state.

  Then, the outer diameter side damper spring 4 and the inner diameter side inner diameter damper spring 28 are connected in series by the outer peripheral side separator 8a and the inner peripheral side separator 8b provided in the intermediate member 31, whereby the input member 1a. , 1b and the damper spring 4 pressed by the spring retainers 7a, 7b are compressed and deformed, and the inner diameter side damper spring 28 is also compressed and transmitted to the output members 2a, 2b. Here, the output members 2a and 2b are guided by the inner peripheral surface of the spacer 32 and are concentric with the output members 1a and 1b.

  FIG. 4 shows a plan view of the annular member 9. On one side of the annular member 9, there are three cutout openings 29, 29..., And the tip of the outer peripheral side separator 8a of the intermediate member 31 passes through the cutout openings 29, 29. Thus, the annular member 9 is attached in alignment. That is, separators 8a, 8a,... Protrude outward in three locations on the damper device 16 shown in the figure so that the separators 8a, 8a,. Are provided with notched openings 29, 29.

  FIG. 5 is an embodiment showing a torque converter provided with another damper device 16 according to the present invention. The basic structure of the damper device 16 is the same as that in FIGS. 1 and 2, but the shapes of the input members 1a and 1b and the annular member 9 are different. The circumferential length of the annular member 9 is longer, so that a region where the annular member 9 covers the damper spring 4 is large.

  Accordingly, not only the outer peripheral side of the damper spring 4 but also both sides can be in contact and restrained. 6 shows a front view of the annular member 9, the annular member 9 also has cutout openings 29, 29... At three locations on one side. In addition, the cut depth of the notch opening 29 is increased so that the tips of the separators 8a, 8a... Of the intermediate member 31 do not interfere with each other during assembly. In the damper device 16 of the torque converter shown in FIG. 5, the input member 1a protrudes outward and sandwiches one side of the annular member 9 with the spring retainer 7a. As described above, by forming the damper spring 4 so that the outer periphery and both sides thereof are in contact with each other, the reduction in hysteresis is increased, and the torsional vibration absorption performance is further improved.

  FIG. 7 is an embodiment showing a torque converter provided with another damper device 16 according to the present invention. The basic structure of the damper device 16 is the same as that in FIGS. 1 and 2, but the shapes of the input members 1a and 1b and the annular member 9 are different. The circumferential length of the annular member 9 is longer than that of the damper device 16 shown in FIG. 5. For this reason, a region where the annular member 9 covers the damper spring 4 is large, and only the outer peripheral side of the damper spring 4 is formed. Instead, both sides can touch and restrain. The annular member 9 is the same as that shown in FIG.

  FIG. 8 shows another embodiment of the damper device of the present invention. The annular member 9 has no cutout on one side as shown in FIG. 4 and has a short cross-sectional circumference on one side that covers the damper spring 4. The absence of the notch increases the rigidity of the annular member and improves the durability. The opposite end is notched and engaged with the upper edge of the input member 1a, so that the annular member 9 and the damper spring 4 are not detached from the damper device. Moreover, the hysteresis is reduced by making the height of the input member 1b low like FIG.5 and FIG.7.

  FIG. 9 is an embodiment showing a torque converter provided with still another damper device 16 of the present invention. The basic structure of the damper device 16 is the same as in the above embodiment, but the shapes of the input members 1a and 1b and the annular member 9 are different. The input members 1 a and 1 b do not restrain the outside of the damper spring 4 but have spring retainers 7 a and 7 b, and restrain the damper spring 4 by the annular member 9.

  That is, the annular member 9 of the damper device 16 has a structure in which the main body member 10 and the auxiliary member 11 are welded and combined, and the restraint area is made larger than in the case of FIG. doing. The annular member 9 is mounted after the damper springs 4, 4... Are arranged at predetermined positions (between the spring pressers 7 provided in the circumferential direction of the input members 1a, 1b), and the main body member 10 and the auxiliary member 9 are supported. The member 11 is welded to each other.

  FIG. 10 is a front view showing the annular member 9, and the annular member 9 does not have a notch opening. That is, since the main body member 10 and the auxiliary member 11 are disposed at predetermined positions and welded to each other, they can be attached without touching the separator 8a or the spring retainer 7 of the intermediate member 31.

  FIG. 11 is a schematic view showing another embodiment of the damper device according to the present invention. When the clutch 19 is turned on, torque is input to the inner diameter side damper springs 28, 28. It is made the structure which outputs from. That is, the input side and the output side are opposite to the damper device 16 shown in the above embodiment. The clutch 19 is connected to plates 34, 34 on which inner diameter side damper springs 28, 28... Are arranged, and a plate 35 on which damper springs 4, 4. .

  The basic structure is the same as that of the damper device 16 shown in the above embodiment, and the input members 34, 34 on the input side are combined with the output members 35, 35 on the output side to provide spacers 36, 36,.・ ・ Guided by and centered. Further, the intermediate member 31 connecting the damper springs 4, 4... And the inner diameter side damper springs 28, 28. The ring-shaped annular member 9 restrains the damper springs 4, 4... Arranged on the outer peripheral side.

  By the way, the torque converter described in the above embodiment constitutes a multi-plate clutch having a plurality of disk plates 23, 23... And a plurality of clutch plates 24, 24. A single-plate clutch configured to engage with the cover is free.

DESCRIPTION OF SYMBOLS 1 Input member 2 Output member 3 Turbine hub 4 Damper spring 5 Drum part 6 Rivet 7 Spring retainer 8 Separator 9 Annular member
10 Body material
11 Auxiliary members
12 coils
13 Pump impeller
14 Turbine runner
15 Stator
16 Damper device
17 Piston
18 outer shell
19 Clutch
20 Front cover
21 Clutch receiver
22 Clutch hub
23 Disc plate
24 Clutch plate
27 Coil spring
28 Inner diameter damper spring
29 Notch opening
30 Spring housing
31 Intermediate member
32 Spacer
34 Input material
35 Output member
36 Spacer















Claims (6)

  1. In a damper device housed in a fluid-filled outer shell such as a torque converter and elastically connecting a transmission input shaft for transmitting power to the transmission and an engine output shaft to absorb torque fluctuation, the damper device includes a plurality of damper devices. The damper springs are arranged on the outer peripheral side so as to be able to expand and contract between the input member and the intermediate member, or between the intermediate member and the output member, and the damper spring is not detached from the input member or the output member. And an annular member that is not involved in torque transmission and is attached to the input member or the output member in a rotatable state. Damper device to do.
  2. The damper device according to claim 1, wherein the annular member is formed so that an outer periphery of the damper spring is in contact therewith.
  3. The damper device according to claim 1, wherein the annular member is shaped so that the outer periphery and both sides of the damper spring, or either one of them is in contact with each other.
  4. The damper device according to claim 1, wherein the annular member is formed so that the outer periphery, both sides, and the inner periphery of the damper spring are in contact with each other.
  5. In a damper device housed in a fluid-filled outer shell such as a torque converter and elastically connecting a transmission input shaft for transmitting power to the transmission and an engine output shaft to absorb torque fluctuation, the damper device includes a plurality of damper devices. A plurality of damper springs are arranged on the outer periphery, a plurality of inner diameter side damper springs are arranged on the inner periphery, and an inner diameter side damper spring is arranged on the inner peripheral surface of the spacer attached to the input member or output member on which the damper springs are arranged. The outer periphery of the output member or the input member is combined to be rotatable concentrically, and the intermediate member for serially connecting the damper spring and the inner diameter side damper spring is rotatably combined. The separator provided is interposed between the damper springs, and the separator provided on the inner periphery is connected to the inner diameter side damper. Interposed between the pulling, further enter the annular member not involved in the transmission of torque to form a ring-shaped space that can be bound fits at least the outer peripheral side portion as the damper spring does not come off of the outer member Alternatively , the damper device is attached to the output member in a rotatable state.
  6. The damper device according to claim 1, 2, 3, 4, or 5, wherein a notch opening is provided on one side of the annular member.


JP2010200644A 2010-09-08 2010-09-08 Damper device Active JP5670676B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019163770A1 (en) 2018-02-20 2019-08-29 ユニプレス株式会社 Torsional vibration reduction device

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5993186B2 (en) * 2012-04-10 2016-09-14 ヴァレオユニシアトランスミッション株式会社 Torsional vibration reduction device and torque converter lockup clutch mechanism using the torsional vibration reduction device
JP5685304B2 (en) 2013-06-04 2015-03-18 株式会社エクセディ Torque converter lockup device
JP5734365B2 (en) * 2013-06-04 2015-06-17 株式会社エクセディ Torque converter lockup device
JP5878893B2 (en) 2013-07-11 2016-03-08 株式会社エクセディ Torque converter lockup device
WO2020096054A1 (en) * 2018-11-08 2020-05-14 ヴァレオカペックジャパン株式会社 Lock-up apparatus for torque converter

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2239928B (en) * 1989-12-21 1993-06-30 Luk Lamellen & Kupplungsbau Apparatus for damping torsion vibrations
JP2002081522A (en) * 2000-09-07 2002-03-22 Exedy Corp Lockup device for torque converter
KR20080066024A (en) * 2005-11-10 2008-07-15 루크 라멜렌 운트 쿠프룽스바우 베타일리궁스 카게 Hydrodynamic torque converter device for an automotive drive train

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019163770A1 (en) 2018-02-20 2019-08-29 ユニプレス株式会社 Torsional vibration reduction device

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