JPS6151685B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a damper disk incorporating an oil-type shock absorber, and its purpose is to effectively absorb torsional vibrations of a drive system and improve starting feeling.

For example, in conventional vehicle clutch disks, friction damper disks using friction washers have been widely used, but in that case, a constant hysteresis occurs regardless of the relative torsional angular velocity of the driving side and driven side. Because you can only get
If a characteristic that improves the starting feeling is selected, a problem arises in that the torsional vibration absorption performance during normal high-speed driving is insufficient.

The present invention attempts to solve the conventional problems by incorporating an oil-type shock absorber into the damper disk, and will be explained below with reference to the drawings.

1 and 2 are vertical cross-sectional partial views of a clutch disk to which the present invention is applied, and FIGS. 1 and 2 show the - and - cross sections of FIG. 3, respectively, and FIG. FIG. 2 is a partial view of FIG. 1 in the direction of the arrows with a portion cut away. A flange 2 of a spline hub 1 that is spline-fitted to an output shaft (not shown in FIG. 1) is connected to a pair of cases 3 and 4 from both sides.
covered with. The cases 3 and 4 have a larger diameter than the flange 2, and the outer peripheries of both cases 3 and 4 are integrally connected by a pin 6 with an annular member 5 and an annular packing 5a in between. The cushioning plate 7 is fixed using this. 8 is a facing fixed to the cushioning plate 7 by rivets 9. Cylindrical flanges 11 and 12 extending inward are formed on the inner peripheral edges of the cases 3 and 4.
is a seal 1 that fits into an annular groove on the outer peripheral surface of the hub 1.
It borders on 3. The cases 3 and 4 are filled with hydraulic oil. 15 is a compression coil spring (torsion spring) extending in the circumferential direction;
As shown in the figure, one window hole 16 is provided in each of the six window holes 16 provided in the flange 2 at equal intervals in the circumferential direction, and as shown in FIG.
The parts protruding from 6 are recesses 17 and 18 shaped to correspond to the springs 15 provided in both cases 3 and 4.
covered with. When the cases 3 and 4 are not twisted relative to the flange 2 as shown in FIG. It is in contact with the inner surfaces 21 and 22.

As shown in FIG. 2, annular members 23 and 24 are disposed between a portion of the flange 2 on the inner circumferential side of the window hole 16 and the inner circumferential portions of the cases 3 and 4 opposing thereto. The annular members 23 and 24 each have an inverted U-shaped cross section and a U-shaped cross section that open toward the flange 2, and are slidable on the flange 2. The annular opening is closed by the flange 2, and an annular chamber is formed inside. 25 and 26 are formed. As shown in FIG. 3, three types of pins 30, 31, and 32 are alternately arranged at intervals in the circumferential direction at nine locations on the inner circumference of the clutch disk. The pins 30 (closing members) are made into a set of two as shown in FIG.
4 are fixed to the cases 3 and 4, respectively, and the large diameter portion 33 is in close contact with the inner surface of the annular members 23 and 24, dividing the entire annular chambers 25 and 26 into partial annular chambers. 34 is an annular seal. As shown in FIG. 1, the pin 31 fixes a cylindrical hydraulic oil compression member 35 on both sides of the flange 2, and the hydraulic oil compression member 35 is slidable on the inner surfaces of the annular members 23 and 24.
The pin 32 in FIG. 1 fits into holes in both the cases 3 and 4 and the annular members 23 and 24 to connect the cases 3 and 4 to each other, and the flange 2 has a circle for inserting the pin 32. A circumferentially long elongated hole 36 (FIG. 3) is provided. In FIG. 1, 37 is a washer, and 38 is an annular seal. 40 is a stopper pin that connects the outer peripheral parts of cases 3 and 4 to each other, and a large diameter pin 41 is fitted into the holes of both cases 3 and 4 from the case 3 side (left side).
and a small diameter pin 42 (screw) screwed into the screw hole of the large diameter pin 41 from the case 4 side (right side),
It passes through a notch 43 provided on the outer circumference of the flange 2. 45 is a washer that also serves as a seal, and 46 is an annular seal. Reference numeral 55 in FIG. 2 is a modification of the stopper pin 40 shown in FIG. 56 is an annular seal.

Next, the operation will be explained. When the clutch is connected and torque in the clutch rotational direction A shown in FIG. 3 is transmitted from the flywheel (not shown) to the facing 8, the torque is introduced into the cases 3 and 4 via the cushioning plate 7, and is further introduced into the recess. 17,18
It is transmitted from the inner surfaces 21 and 22 of the end walls to the side edge 20 of the window hole 16 via the spring 15, and is transmitted from the flange 2 to the hub 1 and the output shaft. When torque is transmitted through the spring 15 in this way,
Since the spring 15 is compressed, cases 3 and 4
is twisted in the direction of rotation A relative to the flange 2, in which case the torque transmitted only through the spring 15 and the twisting angle D increase proportionally, as shown by characteristic X in FIG. On the other hand, in FIG. 5, which shows the negative cross-section of FIG. 23,
24 in the counter-rotational direction (to the left in FIG. 5), and the annular chambers 25a, 2 between the hydraulic oil compression member 35 and the pin 30 (closing member) on the advancing direction side.
Hydraulic oil is compressed within 6a. A part of the compressed hydraulic oil is transferred to the hydraulic oil compression member 35 and the annular member 2.
The annular chambers 25b and 26 are located rearward (to the right) of the hydraulic oil compression member 35 through the narrow gap 47 between 3 and 24.
Some of the hydraulic oil escapes to the annular members 23 and 24.
and the hub 2 through a narrow gap 48 (FIGS. 1 and 2) into a chamber 49 radially outward of the annular members 23, 24. When the hydraulic oil is compressed and passes through the narrow gaps 47 and 48, a resistance force is applied from the hydraulic oil to the hydraulic oil compression member 35 and the pin 30, and a torque corresponding to the resistance force is applied from the pin 30 on the case 3 and 4 side. Hydraulic oil compression member 35 via hydraulic oil,
Since the torque is transmitted to the flange 2, the actual transmitted torque characteristic becomes characteristic Y with hysteresis h occurring in characteristic X, as shown in FIG. Characteristic Y in FIG. 4 shows the case where the torsional angular velocity is constant, but when the torsional angular velocity of the cases 3 and 4 changes and the relative movement speed of the hydraulic oil compression member 35 changes, the oil flows out from the annular chambers 25a and 26a. Since the flow rate of the hydraulic oil changes, the resistance force exerted by the hydraulic oil on the pin 30 and the hydraulic oil compression member 35 also changes, and therefore the hysteresis h also changes in accordance with the torsional angular velocity.

Note that when the torsion angle D reaches a predetermined value dm (d'-m), the stopper pin 40 moves into the notch 4 of the flange 2.
3, and further twisting is prevented.

According to the embodiment of the present invention described above, the annular flange 2 is provided on the outer periphery of the hub 1 connected to the output shaft, and the annular cases 3 and 4 are provided concentrically and relatively rotatably on both sides of the flange 2. Friction facings 8 for introducing torque are connected to the outer peripheries of 3 and 4.

Window holes 16 and depressions 17 are provided at multiple locations facing each other in the axial direction of the flange 2 and the cases 3 and 4, respectively.
18 is provided to form a spring installation chamber, and a compression spring 15 that elastically connects the flange 2 and the cases 3 and 4 in the circumferential direction is arranged in the spring installation chamber.

Annular members 23, 24 are provided between the cases 3, 4 and the flange 2 in a radially inward portion of the spring 15, and the annular members 23, 24 are connected to the cases 3, 4 and the flange 2. Annular chambers 25 and 26 are formed that extend concentrically with the cylindrical chamber 25 and 26. Furthermore, the internal space of the case including the annular chambers 25 and 26 is kept in a liquid-tight state with respect to the external space of the cases 3 and 4 by the packing 5a and the seal 13, so that hydraulic oil does not enter the internal space of the cases 3 and 4. be satisfied.

A hydraulic oil compression member 35 is provided in the annular chambers 25 and 26.
and a closing member 30 are provided at intervals in the circumferential direction. The hydraulic oil compression member 35 and the annular chamber 25,
A narrow gap 47 is formed between the inner surface of 26 and the inner surface of 26. The closing member 30 closes the annular chambers 25 and 26 and has annular chamber portions (25a, 25b, 26a, 26b) located on both sides of the circumferential direction with respect to the member 30.
are maintained in a state in which they are generally not in communication with each other. The hydraulic oil compression member 35 includes the flange 2 and the case 3,
4, and the closing member 30 is fixed to the other of the flange 2 and the cases 3, 4.

In this way, according to the present invention, an oil-type shock absorber is built in and the hysteresis torque changes in response to the torsional angular velocity, so torque fluctuations and vibrations are effectively suppressed at all times during starting and stopping as well as during high-speed operation. can be absorbed into. In addition, the hysteresis characteristics can be easily changed by simply replacing the oil with a different viscosity, and an optimal damper disk can be configured depending on the application.

Note that when embodying the present invention, instead of the illustrated annular members 23 and 24, annular members that open toward the cases 3 and 4 are used, and these annular members and the closing member are fixed to the hub flange 2. At the same time,
The hydraulic oil compression member can also be fixed to the cases 3 and 4. The present invention can also be applied to a disk in which torsion springs act on two or more stages.

[Brief explanation of the drawing]

1 and 2 are longitudinal cross-sectional partial views of the present invention, and FIG. 3 is a partially cutaway partial view in the direction of the arrow in FIG. 1.
FIG. 4 is a graph showing transmission torque-torsion characteristics, and FIG. 5 is a cross-sectional view of FIG. 3. 1... Spline hub, 2... Flange, 3, 4... Case, 8... Friction facing, 13... Seal,
15... Spring, 16... Window hole, 17, 18
... Depression, 23, 24 ... Annular member, 25, 26
...Annular chamber, 35...Hydraulic oil compression member, 30...
Closing member, 47... gap.

Claims (1)

[Claims] 1 An annular flange is provided on the outer periphery of the hub connected to the output shaft, an annular case is provided on both sides of the flange so as to be concentric and relatively rotatable, a friction facing for introducing torque is connected to the outer periphery of the case, and the above flange A spring installation chamber is formed by providing window holes and recesses at multiple locations facing each other in the axial direction of the case, and a compression spring that elastically connects the flange and the case in the circumferential direction is arranged in the spring installation chamber, An annular member extending annularly between the case and the flange is provided in a portion radially inward of the spring, and the annular member forms an annular chamber extending concentrically with the case and the flange, and the case including the annular chamber The internal space is kept liquid-tight with respect to the space outside the case by a seal, the internal space of the case is filled with hydraulic oil, and a hydraulic oil compression member and a closing member are spaced apart in the circumferential direction in the annular chamber. A narrow gap is formed between the hydraulic fluid compression member and the inner surface of the annular chamber, and the annular chamber is closed by the closing member so that the annular chamber portions located on both sides in the circumferential direction with respect to the member are mutually connected. A damper disk characterized in that the hydraulic fluid compression member is fixed to one of the flange and the case, and the closing member is fixed to the other of the flange and the case, the damper disk being maintained in a state of not communicating with each other.