JPH0545287U - Power transmission device - Google Patents

Abstract

(57) [Abstract] [Purpose] To provide a power transmission device capable of effectively absorbing excessive input energy in a transient operating state at the time of starting or stopping an engine. [Structure] The second mass body 8 is elastically connected to the first mass body 2 fixed to the crankshaft 1 by the spring members 13, 13 in the rotating direction, and the first mass body 2 and the second mass body 8 are connected. The rubber-like elastic member 14 that is in sliding contact with at least one of the two mass bodies 2 and 8 when the relative rotation angle thereof is equal to or greater than a predetermined angle is interposed between the both mass bodies 2 and 8.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a power transmission device attached to an end of a crankshaft of an automobile.

[0002]

[Prior Art]

 In recent years, this type of power transmission device effectively absorbs and damps the torsional vibration of the crankshaft due to the fluctuation of the engine rotation, and suppresses the generation of abnormal noise such as gear rattle of transmission gears and so-called muffled noise. , A first mass body fixed to the crankshaft, and a second mass body that is rotatably assembled to the first mass body, and the divided mass bodies are elastically connected by a spring member in the rotation direction. (See Japanese Utility Model Laid-Open No. 60-28650 and Japanese Patent Laid-Open No. 62-204053).

[0003]

[Problems to be solved by the device]

 However, in the power transmission device configured as described above, there may be a case where a rotational fluctuation torque that is equal to or greater than the maximum torque of the engine is input in a transient operating state when the engine is started or stopped. This is because the resonance point of the torsional vibration of the crankshaft system is set so that it normally occurs at a rotational speed equal to or lower than the idle speed of the engine.

Therefore, it is desired to provide a power transmission device having a means for protecting the spring member and the like so that the spring member and the like are not damaged by an excessive input torque in a transient operating state when the engine is started or stopped. Was there.

The present invention has been devised to meet the demand.

[0006]

[Means for Solving the Problems]

 That is, the present invention is a power transmission device in which a first mass body fixed to a crankshaft is elastically connected to a second mass body in a rotation direction by a spring member, and the first mass body and the second mass body are connected to each other. It is characterized in that a rubber-like elastic member, which comes into sliding contact with at least one of both mass bodies when the relative rotation angle of the mass bodies exceeds a predetermined angle, is interposed between both mass bodies.

[0007]

[Action]

 When excessive rotational energy is input to the power transmission device during transient operating conditions such as when the engine is started or stopped, a large friction resistance is generated at the sliding contact part between the rubber-like elastic member and other parts. , Absorbs the excessive input energy.

[0008]

【Example】

 FIG. 1 is a sectional view of a power transmission device according to an embodiment of the present invention in a mounted state. As shown in FIG. 1, an input member 2 as a first mass body is attached to a shaft end of a crankshaft 1 by a bolt 3. It is fixed. Drive plates 4a and 4b are arranged on both sides of the input member 2 so as to be rotatable with respect to the input member 2, and a plurality of stop pins 5 are provided on the inner peripheral side of the pair of drive plates 4a and 4b. The rivets 6 are fixed at intervals and the outer peripheral side is fixed by a plurality of rivets 6. A ring gear 7 meshing with a pinion gear of a starter motor (not shown) is welded to the outer peripheral end of the drive plate 4b, and these drive plates 4a and 4b and the ring gear 7 constitute a second mass body 8. ..

A stopper mechanism 10 is configured by engaging a stop pin 5 with a circumferential groove 9 formed in the input member 2, and the stopper mechanism 10 serves as a drive plate 4 a, 4 b (second mass body). The relative rotation angle of the input member 2 (first mass body) is restricted to a predetermined angle. A bearing 11 is provided between the inner peripheral end of one drive plate 4a and the shoulder portion 2a of the input member 2 so that the drive plates 4a and 4b rotate smoothly with respect to the input member 2. It is devised so that it can be done.

Reference numeral 12 denotes a plurality of spring receiving portions formed in the circumferential direction of the input member 2 (see FIG. 2). The spring receiving portion 12 has a pair of arc-shaped spring members 13, 13 and a position between them. A substantially cylindrical rubber-like elastic member 14 is accommodated via a retainer 15.

Reference numerals 16a and 16b denote spring engaging portions formed on the drive plates 4a and 4b. The spring engaging portions 16a and 16b are formed so as to correspond to the spring receiving portion 12 of the input member 2, and are formed so that a predetermined gap is formed around the rubber-like elastic member 14 and the spring members 13 and 13. I am doing it. A retainer plate 17 is fixed to the inner side walls of the drive plates 4a and 4b between the spring engaging portions 16a and 16b adjacent to each other in the circumferential direction with rivets 18, and the retainer plate 17 is fixed to the input member 2. The arms 2b are engaged with each other with a gap between them (see FIGS. 2 to 4). As a result, the drive plates 4a and 4b and the input member 2 are connected to each other by the pair of spring members 13 and 13 and the rubber-like elastic member 14 arranged between these spring members 13 and 13. The spring receiving portion 12 of the input member 2 contains lubricating grease, and the sealing members 19a and 19b arranged between the input member 2 and the drive plates 4a and 4b prevent the lubricating grease from leaking. ing.

Reference numeral 20 denotes a converter housing of the torque converter 21, and the outer peripheral ends of the drive plates 4 a and 4 b are fixed to the converter housing 20 with bolts 22. A turbine hub 23 is spline-fitted to the output shaft 24. A turbine runner 25 is fixed to a flange portion 23a of the turbine hub 23, and a piston 26 serving as a lockup clutch is attached to the boss portion 23b. Is fitted so that can be slid. The piston 26 has a plurality of claws 27 formed on the back surface thereof engaged with a groove 28 formed on the outer peripheral end of the flange portion 23 a of the turbine hub 23, and therefore rotates integrally with the turbine hub 23. The piston 26 slides to the left side in FIG. 1 when the vehicle speed becomes equal to or higher than a predetermined speed and the oil pressure P ₁ on the back side of the piston 26 becomes larger than the oil pressure P ₂ on the front side of the piston 26. To the inner wall 20a of the converter housing 20 (lock-up).

According to the above-described structure of the embodiment, at the time of low torque input such as lock-up, the spring member 13, the rubber-like elastic member 14, and the rubber-like elastic member 14 are caused by the relative rotation of the input member 2 and the drive plates 4a, 4b. The spring member 13 is compressed between the retainer plate 17 fixed to the drive plates 4a and 4b and the arm portion 2b of the input member 2, and these spring member 13, rubber-like elastic member 14 and spring member 13 act in series. It absorbs and damps the impact force and torsional vibration caused by the fluctuation of the engine rotation. As a result, the dynamic power of the engine is smoothly transmitted from the crankshaft 1 to the converter housing 20 via the power transmission device A, and abnormal noise such as muffled noise in the vehicle compartment is effectively reduced.

In a transient operation state when the engine is started or stopped, the resonance point of the crankshaft system is set so as to occur at a rotation speed equal to or lower than the idle rotation speed of the engine. Is amplified, and a high torque momentarily acts on the power transmission device A. At this time, as shown in FIGS. 5 to 6, the rubber-like elastic member 14 is compressed between the spring member 13 and the spring member 13 as the input member 2 and the drive plates 4a and 4b rotate relative to each other. Then, the rubber-like elastic member 14 is expanded and deformed, and the rubber-like elastic member 14 is pressed against the inner side surfaces of the drive plates 4a and 4b and the peripheral surface 12a of the spring receiving portion of the input member 2, and the rubber-like elastic member 14 and the drive plate 4a. , 4b, a large frictional resistance force (hysteresis torque) is generated, whereby excessive input energy can be absorbed. Therefore, this power transmission device A prevents damage to the spring member 13 and the like due to excessive input torque, and enables smoother and more reliable power transmission.

FIG. 7 is a simple vibration model of a power transmission system in which the power transmission device A of the present embodiment is assembled. In this figure, I1 is the moment of inertia of the input side including the input member 2 and the crankshaft 1, and I2 is The output side moment of inertia of the drive plates 4a, 4b, the ring gear 7, the converter housing 20 and the like, and I3 is the moment of inertia of the output shaft 24 and other power trains that rotate with the output shaft 24. Further, in FIG. 7, K1 is a combined spring constant of the spring members 13, 13 acting in series and the rubber-like elastic member 14 of the power transmission device A, K2 is a combined spring constant of the output shaft 24, and Th is the power. It is a frictional resistance generated in the transmission device A. Incidentally, C0 represents the viscous damping resistance of the engine oil, and C3 represents the viscous damping resistance of the transmission oil. Further, T.sinWt indicates the torque fluctuation of the engine.

FIG. 8 is a diagram comparing a result calculated using the simple vibration model of FIG. 7 with a conventional example. As shown in this figure, this embodiment can reduce the fluctuation torque corresponding to the shaded area.

In the above embodiment, the rubber-like elastic member 14 is slidably contacted with the drive plates 4a, 4b and the spring receiving portion peripheral surface 12a of the input member 2. A frictional resistance force may be generated by sliding only on the peripheral surface 12a. Further, the rubber-like elastic member 14 may be slid only on the inner side surfaces of the drive plates 4a and 4b to generate a frictional resistance force.

[0018]

[Effect of the device]

 As is apparent from the above description, the present invention is a power transmission device in which a first mass body fixed to a crankshaft is elastically connected to a second mass body in a rotating direction by a spring member, Since the rubber-like elastic member that is in sliding contact with at least one of the two mass bodies when the relative rotation angle of the first mass body and the second mass body is equal to or greater than the predetermined angle is interposed between the both mass bodies, Even if excessive rotational energy is input during transient operating conditions such as starting and stopping, it can be absorbed by the large friction resistance generated at the sliding contact part between the rubber-like elastic member and other parts. It enables smoother and more reliable power transmission.

[Brief description of drawings]

FIG. 1 is a sectional view of a power transmission device in an attached state showing an embodiment of the present invention.

FIG. 2 is a front view of the power transmission device with a part cut away.

3 is a sectional view taken along the line BB of FIG.

FIG. 4 is a cross-sectional view taken along the line CC of FIG.

FIG. 5 is a front view of the main parts of the power transmission device when an excessive torque is input.

6 is a cross-sectional view taken along the line DD of FIG.

FIG. 7 is a simplified vibration model diagram of a power transmission system.

FIG. 8 is a diagram showing a relationship between input fluctuation torque and engine speed.

[Explanation of symbols]

1 ... Crank shaft, 2 ... 1st mass body (input member),
8 ... 2nd mass body, 13 ... Spring member, 14 ... Rubber-like elastic member, A ... Power transmission device.

Claims (1)

[Scope of utility model registration request] 1. A power transmission device in which a second mass body is elastically connected to a first mass body fixed to a crankshaft in a rotating direction by a spring member, wherein the first mass body and the second mass body are provided. The power transmission device is characterized in that a rubber-like elastic member that is in sliding contact with at least one of both mass bodies when the relative rotation angle of the mass body is equal to or greater than a predetermined angle is interposed between both mass bodies.