JP2009150471A - Damper device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a damper device capable of appropriately changing torsional rigidity while suppressing the influence of torque fluctuation. <P>SOLUTION: The damper device 1A consists of an input disk 2 and output disk 3 relatively rotatable around an axial line AX, an intermediate disk 4 relatively rotatable around the axial line AX with respect to the disks 2, 3, a pair of coil springs 6, 7 arranged between the protruding part 4a of the intermediate disk 4 and the input disk 2 and output disk 3, a friction generating mechanism 8 for generating friction with respect to relative rotations of the disks 2, 3 and a coupling switching mechanism 40 which contains a coupling key 41 movable between a releasing position allowing relative rotation of the output disk 3 and intermediate disk 4 and a coupling position for relatively non-rotatably coupling the disks 3, 4 and moves the coupling key 41 to the coupling position when the centrifugal force acting on the coupling key 41 is high and to the releasing position when the centrifugal force is low. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a damper device incorporated in a power transmission path of a vehicle.

  As a damper device applied to a clutch assembly of a vehicle, an input rotating body and an output rotating body that can rotate relative to each other, and a low-rigid elastic body and a high-rigid elastic body that are compressed in accordance with the relative rotation of these rotating bodies, In the region where the torsion angle between the rotating bodies is small, rotation is transmitted between the rotating bodies while compressing the low-rigid elastic body, and in the region where the torsion angle between rotating bodies is large, the high-rigid elastic body is compressed and rotated. 2. Description of the Related Art A damper device that changes attenuation characteristics according to a twist angle by transmitting rotation between bodies is known (see, for example, Patent Document 1). In addition, there is Patent Document 2 as a prior art document related to the present invention.

JP 2003-184957 A JP-A-5-256337

  In the conventional damper device, when a high torque is input, the torsion angle increases and the highly rigid elastic body is compressed, thereby increasing the torsional rigidity of the damper device. Therefore, there is a possibility that a sufficient attenuation effect cannot be obtained.

  Therefore, an object of the present invention is to provide a damper device capable of appropriately changing torsional rigidity while suppressing the influence of torque fluctuation.

  The damper device according to the present invention includes a first rotating body and a second rotating body provided so as to be relatively rotatable around a common axis, and a circumferential direction with respect to each of the first rotating body and the second rotating body. An intermediate member provided so as to be relatively displaceable, a pair of elastic bodies respectively disposed between the intermediate member and the first rotating body and the second rotating body so as to sandwich the intermediate member, and the first Friction generating means for generating friction with respect to relative rotation between the rotating body and the second rotating body, and relative rotation between the rotating body of either the first rotating body or the two rotating bodies and the intermediate member. A connecting member that can move between a permissible release position and a connecting position that connects the one rotating body and the intermediate member so as not to be relatively rotatable, and when the centrifugal force acting on the connecting member is high, With the connecting member at the connecting position, the centrifugal force is low. When it is obtained by a coupling switching mechanism for moving each of said release position (claim 1).

  According to the damper device of the present invention, when the rotation speeds of the first rotating body and the second rotating body are low, the connecting member is in the release position, and the intermediate member is relative to both the first rotating body and the second rotating body. It can be displaced relative to the circumferential direction. Therefore, torque is transmitted between the first rotating body and the second rotating body via one elastic body, the intermediate member, and the other elastic body. When the first rotating body and the second rotating body rotate relative to each other due to torque fluctuation, the vibration is attenuated by the expansion and contraction of the pair of elastic bodies and the friction generated by the friction generating means. When the rotational force increases and the centrifugal force acting on the connecting member increases, the connecting member moves to the connecting position, and either the first rotating body or the second rotating body and the intermediate member are relative to each other. It is non-rotatably connected. Therefore, only one elastic body is taken into the torque transmission path between the first rotating body and the second rotating body, and the other elastic body is excluded from the torque transmission path. As a result, the torsional rigidity between the first rotating body and the second rotating body is lower than the torsional rigidity when the connecting member is in the release position. As described above, in the damper device according to the present invention, the torsional rigidity is switched by utilizing the centrifugal force acting on the connecting member. Therefore, the torsional rigidity is controlled according to the rotational speed while suppressing the influence of the torque fluctuation on the torsional rigidity. Can be changed.

  In one aspect of the present invention, each of the first rotating body and the second rotating body is provided with an elastic body accommodating portion that accommodates the pair of elastic bodies, and the intermediate member includes the elastic body. A projecting portion projecting into the body housing portion may be provided, and the pair of elastic bodies may be arranged in the elastic body housing portion so as to be distributed in the circumferential direction across the projecting portion. . By arranging the elastic body in this way, when the connecting member is in the release position, torque can be transmitted between the first rotating body and the second rotating body via the intermediate member and the pair of elastic bodies. When the connecting member is in the connecting position, torque can be transmitted between the one rotating body and the protruding portion of the intermediate member without using an elastic body.

  In one embodiment of the present invention, the connection switching mechanism is provided in either one of the one rotating body or the intermediate member and can receive the whole of the connection member at the release position, A key groove that is provided on either the rotating body or the intermediate member so as to be continuous with the radially outer peripheral side of the guide groove, and into which a part of the connection member at the connection position is fitted, and the connection member And a return spring that generates a spring force to be held in the guide groove. According to this embodiment, in the region where the rotational speed is low, the entire connecting member is held at the release position in the guide groove by the force of the return spring, and when the rotational speed increases, the connecting member moves in the guide groove by centrifugal force. Part of it fits into the keyway. As a result, the intermediate member and the one rotating body are connected so as not to be relatively rotatable.

  In one embodiment of the present invention, the first rotating body or the second rotating body is connected to an output shaft of an internal combustion engine mounted as a prime mover in a vehicle, and the connecting member has a low output shaft whose idling speed is equal to or less than the idling speed. It may be held at the release position when rotating in a rotation range, and may move to the connection position when the output shaft rotates in a high rotation range higher than the idling rotational speed ( Claim 4). According to this, the torsional rigidity of the damper device is reduced and the vibration damping effect is enhanced in a low rotation range such as when the internal combustion engine is started, stopped, or idling, while on the other hand, the response is high as in acceleration. In the high rotation range where the high-speed rotation is required, the torsional rigidity of the damper device is increased, and the responsiveness requirement is satisfied. Even in an operating state where the rotation is low and the torque fluctuation is large as at the time of starting, the torsional rigidity can be kept low to prevent the vibration damping effect from deteriorating.

  As described above, in the damper device according to the present invention, the connecting member is moved from the release position to the connecting position by centrifugal force to connect the one rotating body and the intermediate member so as not to be relatively rotatable, thereby the damper. Since the torsional rigidity of the device is increased, it is possible to change the torsional rigidity according to the rotational speed while suppressing the influence of torque fluctuation on the torsional rigidity.

[First embodiment]
FIG. 1 is a partially cutaway front view in the axial direction of a damper device according to a first embodiment of the present invention. The illustrated damper device 1A is provided between an output shaft of an internal combustion engine mounted on a vehicle as a prime mover and an input shaft of a transmission, and includes an input disk 2 as a first rotating body, and a second rotating body. As an output disk 3, an intermediate disk 4 as an intermediate member disposed between these disks 2, 3, and a plurality of groups (four groups in the figure) disposed between these disks 3, 4, 5 Coil springs 6 and 7 are provided. A set of coil springs 6 and 7 corresponds to a pair of elastic bodies. The input disk 2 and the output disk 3 can be rotated relative to each other about a common rotation axis AX. The intermediate disk 4 can rotate relative to the input disk 2 and the output disk 3 around the axis AX. In other words, the intermediate disk 4 can be displaced relative to the input disk 2 and the output disk 3 in the circumferential direction. The shapes, dimensions and spring constants of the springs 6, 7 can be equal to each other.

  As shown in FIG. 2, the input disk 2 includes a ring-shaped joint portion 10 disposed on the outer periphery thereof, a pair of outer plates 11 disposed parallel to each other on the inner periphery of the joint portion 10, and the joint portion 10. A connecting plate 12 disposed between the outer plate 11 and the outer plate 11 is provided. The joint portion 10 has a configuration in which two ring plates 10a and 10b are joined in a non-separable manner, and the ring plates 10a and 10b are coupled to an output shaft of the internal combustion engine so as to be integrally rotatable. The ring plates 10a and 10b and the connecting plate 12 are fastened via a torque limiting mechanism 13 so that the torque to be transmitted is integrally rotatable within a range that does not exceed a predetermined allowable value. The inner periphery of the connecting plate 12 is joined to the outer plate 11 so as to be integrally rotatable.

  On the other hand, the output disk 3 includes a hub 20 disposed at the center of the damper device 1A and a pair of inner plates 21 disposed on the outer periphery of the hub 20 in parallel with each other. The hub 20 is formed with a through hole 20a into which the transmission-side input shaft is fitted. The center line of the through hole 20a corresponds to the axis AX of the damper device 1A. The inner plate 21 is arranged in parallel with an appropriate gap inside the outer plate 11 of the input disk 2. A flange 22 is integrally formed on the outer periphery of the hub 20, and an inner plate 21 is joined to the flange 22 so as to be integrally rotatable. The intermediate disk 4 is disposed between the inner plates 21 of the output disk 3 and on the outer periphery of the flange 22. The intermediate disk 4 can rotate relative to the inner plate 21 and the flange 22 around the axis AX. Further, a friction generating mechanism 8 is provided between the outer plate 11 and the inner plate 21 to generate friction against the relative rotation of the two.

  Returning to FIG. 1, the description will be continued. On the outer periphery of each of the outer plate 11 and the inner plate 21, a plurality (four in the figure) of spring accommodating portions 11a and 21a for receiving the springs 6 and 7 are provided at equal intervals in the circumferential direction. The spring accommodating portions 11a and 21a correspond to elastic body accommodating portions. The spring accommodating portion 11a of the outer plate 11 is formed by punching the outer plate 11 into a window shape, and the spring accommodating portion 21a of the inner plate 21 is formed by cutting the inner plate 21 to the outer periphery in the radial direction. The circumferential lengths of the spring accommodating portion 11a and the spring accommodating portion 21a are equal to each other. On the outer periphery of the intermediate disk 4, a protrusion 4a for receiving the springs 6 and 7 is provided so as to protrude to the outer periphery in the radial direction.

  The outer plate 11 and the inner plate 21 are combined so that their spring accommodating portions 11a and 21a are aligned at the same position in the circumferential direction. The intermediate disc 4 is combined so that the protruding portion 4a is positioned at the substantially center in the circumferential direction of the spring accommodating portions 11a and 21a. The spring 6 is arranged on one side of the protrusion 4a in the circumferential direction (clockwise in the figure), and the spring 7 is arranged on the other side in a slightly compressed state. An outer spring receiver 30 and an inner spring receiver 31 are disposed at both ends of the springs 6 and 7, and an inner spring receiver 32 and an outer spring receiver 33 are disposed at both ends of the spring 7. The outer spring receivers 30 and 33 are provided so as to reach the outer plate 11 on the other side via the pair of inner plates 21 from the outer plate 11 on one side in the direction of the axis AX. On the other hand, the inner spring receivers 32 and 33 abut only on the protrusion 4a. Thereby, the repulsive force against the compression of the springs 6 and 7 acts on the outer plate 11 and the inner plate 21 equally via the outer spring receivers 30 and 33. The outer spring receivers 30 and 33 are immovable in the radial direction by meshing with the claws 11b and 21b formed on the outer plate 11 and the inner plate 21, respectively. It cannot move in the radial direction by meshing with 4b.

  The damper device 1A is provided with four connection switching mechanisms 40 so as to make a pair with the spring accommodating portion 21a of the inner plate 21. The connection switching mechanism 40 is provided to switch the intermediate disk 4 and the output disk 3 between a state where relative rotation is allowed and a state where relative rotation is impossible. The details of one connection switching mechanism 40 are shown in FIG. The other connection switching mechanisms 40 have the same configuration. The connection switching mechanism 40 includes a key 41 as a connecting member housed in the guide groove 21 c of the inner plate 21, and a return spring 42 that pulls the key 41 toward the center side in the radial direction of the inner plate 21. The guide groove 21c extends in the radial direction of the inner plate 21, and the outer end of the guide groove 21c opens at the center in the circumferential direction of the spring accommodating portion 21a. A key groove 4 c that can receive the key 41 is formed on the inner periphery of the intermediate disk 4. When the protruding portion 4a of the intermediate disk 4 is located at the center in the circumferential direction of the spring accommodating portion 21a, the key groove 4c is connected in a straight line to the radially outer peripheral side of the guide groove 21c. Thereby, the key 41 is movable between a release position where the entire key 41 enters the guide groove 21c and a connecting position where a part of the key 41 protrudes from the guide groove 21c and enters the key groove 4c. As is clear from FIG. 2, the key 41 is disposed so as to straddle between the pair of inner plates 21.

  Next, the operation of the damper device 1A will be described. Consider a case where a counterclockwise torque T is input to the input disk 2 of the damper device 1A as shown in FIG. However, it is assumed that the connecting key 41 is in a release position, that is, a position not engaged with the key groove 4c. In this case, torque T is transmitted from the outer plate 11 to the outer spring receiver 30, and the torque T passes through the spring 6, the inner spring receiver 31, the protrusion 4 a of the intermediate disk 4, the inner spring receiver 32, the spring 7 and the outer spring receiver 33. The torque T is output from the hub 20 of the output disk 3 by being sequentially transmitted to the inner plate 21. When torque fluctuation occurs, the springs 6 and 7 expand and contract, and at the same time, the vibration energy is absorbed by the friction applied by the friction generating mechanism 8, and the vibration is attenuated. That is, in a state where the connection key 41 is in the release position, the springs 6 and 7 are taken in series in the torque transmission path, and the springs 6 and 7 and the friction generating mechanism 8 constitute a damping mechanism.

  The connection key 41 is held at the release position by the tensile force of the return spring 42. When the disks 2 and 3 rotate, a centrifugal force proportional to the square of their rotation speed acts on the connection key 41. When the centrifugal force exceeds the pulling force of the return spring 42, the connection key 41 moves to the connection position. As a result, the intermediate disk 4 and the output disk 3 are connected so as not to be relatively rotatable. In this case, until the torque T is transmitted from the outer plate 11 to the intermediate disk 4 via the outer spring receiver 30, the spring 6, and the inner spring receiver 31 in sequence, the same as when the connecting key 41 is in the release position, Since the intermediate disk 4 and the inner plate 21 are not relatively rotatable, the torque T is directly transmitted from the intermediate disk 4 to the inner plate 21 via the connection key 41. As a result, the spring 7 is excluded from the torque transmission path, and the spring 6 and the friction generating mechanism 8 constitute a damping mechanism. In this case, the torsional rigidity of the damper device 1A is higher than the torsional rigidity when the connecting key 41 is in the release position as a result of the spring 7 being excluded from the torque transmission path.

  When the direction of torque applied to the input disk 2 is reversed, torque is transmitted from the outer plate 11 to the inner plate 21 via the spring 7, the intermediate disk 4, and the spring 6, and the intermediate disk is connected by the connecting key 41. 4 and the output disk 3 are connected so as not to rotate relative to each other, torque is transmitted from the outer plate 11 to the inner plate 21 via the spring 7 and the intermediate disk 4, and the spring 6 is excluded from the torque transmission path. That is, only the spring 6 and the spring 7 are functionally interchanged, and the springs 6 and 7 are the same, so the torsional rigidity of the damper device 1A does not vary depending on the rotation direction.

  FIG. 3 shows the relationship between the torsional rigidity K of the damper device 1A and the rotational speed of the output shaft of the internal combustion engine to which the input disk 2 is connected. If the spring constant of the spring 6 is k1 and the spring constant of the spring 7 is k2 (for example, k1 = k2 = k), the torsional rigidity K when the connecting key 41 is in the release position is given by the following equation (1). The torsional rigidity K when the connection key 41 is in the connection position is given by the following equation (2).

  Therefore, when the rotational speed of the output shaft of the internal combustion engine connected to the input disk 2 is low, the torsional rigidity K becomes a low value of the equation (2), and when the rotational speed increases, the torsional rigidity K increases. The engine speed NEth, which is a threshold value at which the torsional rigidity is switched, is set somewhat higher than, for example, the idling speed of the internal combustion engine. As a result, in the start, stop, or idling region of the internal combustion engine, the torsional rigidity of the damper device 1A is reduced to increase the vibration damping effect, while the high rotation region where high responsiveness is required as in acceleration. Then, the torsional rigidity of the damper device 1A can be increased to satisfy the responsiveness requirement. In addition, since the torsional rigidity is switched depending on the rotation speed, there is an advantage that the torque fluctuation is not affected. For example, it is possible to keep the torsional rigidity low and prevent the vibration damping effect from deteriorating even in an operating state where the rotation is low and the torque fluctuation is large, such as when starting.

[Second form]
FIG. 5 is a partially broken front view in the axial direction of the damper device according to the second embodiment of the present invention, and FIG. 5 is an enlarged view of a part thereof. 5 and 6, the same reference numerals are given to portions common to FIGS. 1 to 3, and description thereof is omitted. The damper device 1B of the present embodiment is different from the damper device 1A of the first embodiment in that the connection key 41 of the connection switching mechanism 40 is disposed between the input disk 2 and the intermediate disk 4. That is, in the connection switching mechanism 40 of the damper device 1B, the guide groove 4d is formed in the protrusion 4a of the intermediate disk 4, and the connection key 41 is accommodated in the guide groove 4d. A key groove 12a is formed in the connecting plate 12 of the input disk 2 with its circumferential position aligned with the guide groove 4d. The connection key 41 is moved between a release position where the entire connection key 41 is retracted into the guide groove 4d by the pulling force of the return spring 42 and a connection position where a part of the connection key 41 protrudes from the guide groove 4d by centrifugal force and partially enters the key groove 12a. Is possible.

  In this embodiment, the connection key 41 is held at the release position in the guide groove 4d of the intermediate disk 4 in the region where the rotational speed of the internal combustion engine is low. In this case, the counterclockwise torque T is output from the input disk 2 via the outer spring receiver 30, the spring 6, the inner spring receiver 31, the intermediate disk 4, the inner spring receiver 32, the spring 7 and the outer spring receiver 33 in order. It is transmitted to the disk 3. Since the springs 6 and 7 are taken into the torque transmission path in series, the torsional rigidity is as in the above equation (1). On the other hand, when the rotational speed of the internal combustion engine increases, the connecting key 41 moves to the connecting position by centrifugal force and fits into the key groove 12a, and the input disk 2 and the intermediate disk 4 are connected so as not to be relatively rotatable. In this case, the counterclockwise torque T is directly transmitted from the input disk 2 to the intermediate disk 4 without passing through the spring 6, and from the intermediate disk 4 to the inner spring receiver 32, the spring 7 and the outer spring receiver 33. Are sequentially transmitted to the output disk 3. Since only one spring 7 exists in the torque transmission path at this time, the torsional rigidity is expressed by the above equation (2). Therefore, also in this embodiment, the torsional rigidity of the damper device 1B can be switched in accordance with the number of rotations as in the first embodiment. When the transmission direction of the torque T is reversed, the spring 6 and the spring 7 are only functionally interchanged, and the springs 6 and 7 are the same, so the torsional rigidity of the damper device 1B varies depending on the rotational direction. There is nothing.

  The present invention is not limited to the above form and can be implemented in various forms. For example, the connecting member is located at the release position in a region where the centrifugal force does not act or is relatively small, and allows relative rotation between the first or second rotating body and the intermediate member, and the centrifugal force is relatively low. The first or second rotating body and the intermediate member may be connected so as not to be relatively rotatable by moving to the connecting position when they are increased. The modification is shown in FIGS. In this example, a guide groove 21d and a key groove 4e are formed on the opposing surfaces of the output disk 3 and the intermediate disk 4, and a connecting key 41 is fitted between these grooves. The guide groove 21d on the output disk 3 side is formed with substantially the same width as the thickness of the connection key 41 so as to allow only the movement of the connection key 41 in the radial direction. On the other hand, the key groove 4e is formed sufficiently wider than the connection key 41 in the circumferential direction so that relative rotation of the disks 3 and 4 is allowed on the radial center side, and on the radially outer side, the key grooves 4e are formed. The groove width is narrowed to the same extent as the connecting key 41 so that relative rotation is impossible. The connection key 41 is drawn to the release position on the radial center side by a return spring 42 disposed in the guide 21d. Also in this example, the connection key 41 moves between the release position and the connection position in accordance with the rotational speed of the disks 3 and 4, and the torsional rigidity is switched. As a further modification of FIGS. 7 and 8, a guide groove similar to the guide groove 21 d may be formed in the input disk 2 instead of the output disk 3, or the guide groove may be formed in the intermediate disk 4. Alternatively, a keyway may be formed in the input disk 2.

  In the present invention, the elastic body is not limited to the coil spring, and an elastic body made of an elastic material such as rubber or elastomer may be disposed between the first and second rotating bodies and the intermediate member. The elastic body may be arranged to be deformed in tension during torque transmission. The friction generating means is not limited to an example provided as a mechanism or member different from the elastic body. For example, by using a vibration-proof rubber having a large internal friction loss as an elastic body, the elastic body may function as a friction generating means. The intermediate member is not limited to the disc shape, and it is sufficient that the intermediate member can be relatively displaced in the circumferential direction with respect to both the first rotating body and the second rotating body. For example, in the above embodiment, an intermediate member as a separate member may be disposed so as to be relatively displaceable in the circumferential direction for each of the spring accommodating portions 11a and 21a, and the springs 6 and 7 may be disposed on both sides thereof.

The partially broken front view in the axial direction of the damper apparatus which concerns on the 1st form of this invention. Sectional drawing along the II-II line of FIG. The enlarged view of the III section of FIG. The figure which shows the relationship between the torsional rigidity of a damper, and an engine speed. The partially broken front view in the axial direction of the damper apparatus which concerns on the 2nd form of this invention. The enlarged view of the VI section of FIG. The figure which shows the modification of a connection switching mechanism. Sectional drawing along the VIII-VIII line of the figure in the connection switching mechanism of FIG.

Explanation of symbols

1A, 1B Damper device 2 Input disk (first rotating body)
3 Output disk (second rotating body)
4 Intermediate disc (intermediate member)
4a Protruding part 4c Key groove 4d Guide groove 4e Key groove 6, 7 Coil spring (elastic body)
8 Friction generating mechanism 10 Joining portion 11 Outer plate 11a Spring accommodating portion (elastic body accommodating portion)
12 connecting plate 12a keyway 20 hub 21 inner plate 21a spring accommodating portion (elastic body accommodating portion)
21c guide groove 21d guide groove 30, 33 outer spring receiver 31, 32 inner spring receiver 40 connection switching mechanism 41 key (connection member)
42 Return spring AX Common axis

Claims (4)

A first rotating body and a second rotating body provided so as to be relatively rotatable around a common axis;
An intermediate member provided so as to be relatively displaceable in the circumferential direction with respect to each of the first rotating body and the second rotating body;
A pair of elastic bodies disposed between the intermediate member and the first and second rotating bodies so as to sandwich the intermediate member,
Friction generating means for generating friction with respect to relative rotation between the first rotating body and the second rotating body;
A release position that allows relative rotation between one of the first rotating body or the two rotating bodies and the intermediate member, and a connection that connects the one rotating body and the intermediate member so as not to be relatively rotatable. A connection switch that has a connecting member that can move between positions, and moves the connecting member to the connecting position when the centrifugal force acting on the connecting member is high, and to the release position when the centrifugal force is low. Mechanism,
Damper device with   Each of the first rotating body and the second rotating body is provided with an elastic body accommodating portion that accommodates the pair of elastic bodies, and the intermediate member protrudes into the elastic body accommodating portion. 2. The damper device according to claim 1, wherein a portion is provided, and the pair of elastic bodies are arranged in the elastic body accommodating portion so as to be distributed in the circumferential direction with the protruding portion interposed therebetween.   The connection switching mechanism is provided in either one of the one rotating body or the intermediate member and can receive the entire connecting member at the release position; and the one rotating body or the intermediate member A key groove that is provided on the other side so as to be continuous with the radially outer peripheral side of the guide groove and into which a part of the connection member at the connection position is fitted, and a spring that holds the connection member in the guide groove The damper device according to claim 1, further comprising a return spring that generates force.   When the first rotating body or the second rotating body is connected to an output shaft of an internal combustion engine mounted on a vehicle as a prime mover, and the connecting member is rotating in a low rotation range where the output shaft is equal to or less than the idling rotational speed. The damper according to any one of claims 1 to 3, wherein the damper is held at the release position and moves to the connection position when the output shaft rotates in a high rotation range higher than the idling rotation speed. apparatus.

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