JP2007315416A - Viscous rubber damper - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a viscous rubber damper which can obtain a great vibration damping force by setting the viscous resistance larger which a viscous fluid can generate. <P>SOLUTION: A viscous rubber damper forms a sealed space 6 surrounded by a hub 2, a pair of rubbers 4, 5 and an inertial mass 3 for a rubber by connecting the inertial mass 3 for a rubber to the hub 2 through the medium of a pair of damper rubbers 4, 5. While rotatably assembling an inertial mass 7 for a viscous in the sealed space 6, minute clearances 8, 9, 10, 11 are respectively set between the inertial mass 7 for a viscous and hub 2 and between the inertial mass 7 for a viscous and inertial mass 3 for a rubber. Viscous fluid 16 is sealed in the sealed space 6. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a viscous rubber damper used to absorb and damp torsional vibrations generated on a rotating shaft such as a crankshaft of an internal combustion engine. The viscous rubber damper of the present invention is used not only for a crank pulley portion of an automobile engine, but also for an internal combustion engine other than an automobile, various engines that need to transmit driving force while absorbing torsional vibration, and the like.

  Conventionally, as shown in the sectional view of FIG. 4A and the schematic diagram of FIG. 4B, a lid member 53 is combined with the hub 52 to form an annular sealed space 54, and the hub 52 is formed in the sealed space 54. There is known a viscous rubber damper 51 in which an inertial mass 56 is connected via a damper rubber 55 and a viscous fluid 57 is enclosed (see Patent Document 1). The viscous rubber damper 51 constitutes a resonance system that resonates with respect to vibration of a certain frequency by the spring constant of the damper rubber 55 and the inertial mass of the inertial mass 56. In contrast, the vibration damping force is increased by the viscous resistance of the viscous fluid 57 generated when the inertial mass 56 is relatively displaced in the circumferential direction. In the schematic diagram of FIG. 4B, the rubber damper portion connected by the damper rubber 55 is indicated by symbol a, the viscous damper portion by interposing the viscous fluid 57 is indicated by symbol b, and the basic structure of the crank system is indicated by symbol c. Each is shown.

  However, in the above prior art, since the inertia mass 56 is connected to the hub 52 via the damper rubber 55, the inertia mass 56 is displaced relative to the hub 52 only within a range in which the damper rubber 55 is elastically deformed. The relative displacement (angle) with respect to the hub 52 is substantially restricted. Further, as described above, the inertia mass 56 resonates, so that the viscous resistance due to the viscous fluid 57 is generated only at the time of the resonance operation. Therefore, the above-described prior art has the disadvantage that the viscous resistance that can be generated by the viscous fluid 57 is not so large, and therefore the vibration damping force is small.

Japanese Utility Model Publication No. 3-7562

  In view of the above points, an object of the present invention is to provide a viscous rubber damper in which a viscous resistance that can be generated by a viscous fluid can be set large, and a large vibration damping force can be obtained.

  In order to achieve the above object, the viscous rubber damper according to the present invention is a sealed space surrounded by the hub, the pair of damper rubbers, and the rubber inertia mass by connecting the rubber inertia mass to the hub via the pair of damper rubbers. Forming a viscous inertia mass rotatably in the sealed space, and setting minute gaps between the viscous inertia mass and the hub and between the viscous inertia mass and the rubber inertia mass, respectively, It is characterized in that a viscous fluid is sealed in the space.

  The present invention has the following effects.

That is, in the viscous rubber damper of the present invention having the above-described configuration, the inertia mass for viscous that is incorporated in a sealed space surrounded by the hub, the pair of damper rubbers, and the inertial mass for rubber is connected to the inertial mass for the hub and rubber via the damper rubber. The viscous inertia mass can be freely rotated with respect to these parts. In addition, since the viscous inertia mass is displaced relative to the hub and rubber inertia mass in the circumferential direction, there is an opportunity to generate viscous resistance due to the viscous fluid other than during the resonance operation of the rubber inertia mass. ing. For example, as shown in the graph of FIG. 3, when the resonance frequency of the resonance system composed of the damper rubber and the rubber inertia mass is set in accordance with the torsional vibration peak P in the curve a without damper, As shown in the figure, two lower peaks P ₁ and P ₂ are newly generated. Even at the latter peaks P ₁ and P ₂ , the viscous resistance due to the viscous fluid is generated according to the present invention. It is possible to reduce torsional vibration over a wide range of numbers. Therefore, according to the present invention, it is possible to generate a large viscous resistance as compared with the prior art and increase the vibration damping force. In addition, when a large viscous resistance is generated by the viscous fluid in this way, input to the rubber rubber of the rubber damper portion is reduced, so that a margin for durability of the rubber damper can be increased.

  The present invention includes the following embodiments.

Constitution···
(1) A viscous rubber damper is characterized by having a rotating viscous mass and a swinging rubber damper mass.
(2) In order to increase the viscous viscosity resistance, not only rocking but also rotating the mass to obtain a large viscous resistance.
(3) As shown in the schematic diagram of FIG. 2, the present invention exhibits further vibration damping properties by adding damping even between the rubber mass and the viscous mass.

effect···
(4) The torsional vibration can be further reduced by increasing the viscous resistance.
(5) Also, the rubber damper part has less input to the rubber, and the durability margin is further increased.

  Next, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 shows a half-cut section of a viscous rubber damper 1 according to an embodiment of the present invention. The viscous rubber damper 1 is connected to a hub 2 via a pair of damper rubbers 4 and 5, and an inertia mass for rubber (first ) 3 is connected to form a sealed space 6 surrounded by the hub 2, the pair of damper rubbers 4, 5 and the rubber inertia mass 3, and the viscous inertia mass (second vibration) is formed in the sealed space 6. Ring) 7 is rotatably incorporated and minute gaps 8, 9, 10, and 11 are set between the viscous inertia mass 7 and the hub 2 and between the viscous inertia mass 7 and the rubber inertia mass 3, respectively. 6 is characterized in that a viscous fluid (viscous liquid) 16 is sealed.

  Details of each component are as follows.

  That is, first, the hub 2 is formed in an annular shape from a predetermined metal and has a boss portion 2a attached to a rotating shaft such as a crankshaft of an internal combustion engine. The boss portion 2a has an inner peripheral cylindrical portion 2b and an end surface portion. 2c and outer peripheral cylinder part 2d are integrally molded. That is, the inner peripheral cylindrical portion 2b is integrally formed on the outer peripheral side of the boss portion 2a in the axial direction (leftward in the figure), and radially outward at one end in the axial direction of the inner peripheral cylindrical portion 2b. An end surface portion 2c is integrally formed toward the outer periphery, and an outer peripheral cylindrical portion 2d is integrally formed at the outer peripheral end portion of the end surface portion 2c toward the other axial direction (rightward in the drawing). The inner peripheral cylindrical portion 2b, the end surface portion 2c and the outer peripheral cylindrical portion 2d are formed in a substantially U-shaped cross section as a whole.

  The rubber inertia mass 3 is formed in a ring shape from a predetermined metal and is disposed on the outer peripheral side of the inner peripheral cylindrical portion 2b of the hub 2 and on the other axial end of the small diameter cylindrical portion 3a. An end surface portion 3b integrally molded outward in the radial direction and a large-diameter cylindrical portion 3c integrally molded toward the one axial direction at the outer peripheral end portion of the end surface portion 3b are integrally provided. The large-diameter cylindrical portion 3c is disposed on the outer peripheral side of the outer peripheral cylindrical portion 2d of the hub 2, and a pulley groove 3d for winding an endless belt is provided on the outer peripheral surface to transmit the rotational torque to the auxiliary device. Yes. The small-diameter cylindrical portion 3a, the end surface portion 3b, and the large-diameter cylindrical portion 3c are formed in a substantially U-shaped cross section as a whole.

  Of the pair of damper rubbers 4 and 5, the damper rubber 4 on the inner peripheral side is formed in a ring shape by a predetermined rubber-like elastic body, and the inner peripheral cylindrical portion 2 b of the hub 2 and the small diameter cylindrical portion 3 a of the rubber inertia mass 3. It is press-fitted between. The damper rubber 5 on the outer peripheral side is also formed in a ring shape from a predetermined rubber-like elastic body, and is press-fitted between the outer peripheral cylindrical portion 2d of the hub 2 and the large-diameter cylindrical portion 3c of the rubber inertia mass 3. A rubber inertia mass 3 is connected to the hub 2 via the pair of damper rubbers 4 and 5 by press-fitting the pair of inner and outer damper rubbers 4 and 5, and the sealed space 6 is formed.

  The viscous inertia mass 7 is formed in an annular shape from a predetermined metal and is inserted into the sealed space 6 so as to be freely rotatable. Further, the viscous inertia mass 7 is formed in a substantially rectangular cross section, has one end surface 7a in the axial direction opposed to the end surface portion 2c of the hub 2 in the axial direction, and has an outer peripheral surface 7b and the outer peripheral cylindrical portion 2d of the hub 2. Opposite to the radial direction, the other axial end surface 7c faces the end surface portion 3b of the rubber inertia mass 3 in the axial direction, and the inner peripheral surface 7d faces the small diameter cylindrical portion 3a of the rubber inertia mass 3 in the radial direction. , Minute gaps 8, 9, 10, and 11 are set between the counterparts.

  Further, bearings 12, 13, 14, and 15 are arranged around the viscous inertia mass 7 so that the viscous inertia mass 7 does not interfere with the hub 2 and the rubber inertia mass 3. The bearings 12, 13, 14, and 15 are provided between one end surface 7 a of the viscous inertia mass 7 in the axial direction and the end surface portion 2 c of the hub 2, between the outer peripheral surface 7 b of the viscous inertia mass 7 and the outer peripheral cylindrical portion 2 d of the hub 2. Between the other axial end surface 7c of the viscous inertia mass 7 and the end surface portion 3b of the rubber inertia mass 3, and between the inner peripheral surface 7d of the viscous inertia mass 7 and the small diameter cylindrical portion 3a of the rubber inertia mass 3. The viscous inertia mass 7 can be positioned if there is only one radial bearing 13, 15, but only one of them may be provided.

  The viscous fluid 16 is made of silicon oil or the like, and is fully filled in the sealed space 6 in which the viscous inertia mass 7 and the bearings 12, 13, 14, 15 are inserted. The filling (sealing) of the viscous fluid 16 is carried out by providing two holes for vacuum injection at an arbitrary position of the hub 2 or the rubber inertia mass 3 after press-fitting in the liquid or rubber 4 or 5.

  When the viscous rubber damper 1 having the above-described configuration is schematically shown in FIG. 2, the masses 3 and 7 are divided into two in comparison with the conventional system shown in FIG. Also, a viscous damper portion b is set.

In this viscous rubber damper, the rubber inertia mass 3 is connected to the hub 2 via a pair of damper rubbers 4 and 5, thereby being surrounded by the hub 2, the pair of damper rubbers 4 and 5, and the rubber inertia mass 3. The viscous inertia mass 7 is rotatably incorporated in the sealed space 6. The viscous inertia mass 7 is connected to the hub 2 and the rubber inertia mass 3 via damper rubber. It is not possible to rotate freely with respect to these parts. Further, since the viscous inertia mass 7 can be displaced relative to both the hub 2 and the rubber inertia mass 3 in the circumferential direction, the viscous resistance caused by the viscous fluid 16 is not limited to when the rubber inertia mass 3 is in resonance. An opportunity to generate is set. For example, in the graph showing the relationship between the engine speed and the crankshaft torsional vibration in FIG. When the resonance frequency is set, two lower peaks P ₁ and P ₂ are newly generated by the resonance operation as shown in the curve B. Even at the latter peaks P ₁ and P ₂ , Accordingly, since viscous resistance is generated by the viscous fluid 16, it is possible to reduce torsional vibration over a wide range of engine speed. Therefore, from these facts, it is possible to generate a large viscous resistance as compared with the conventional case and to increase the vibration damping force. In addition, when a large viscous resistance is generated by the viscous fluid 16 in this way, the input to the rubber rubbers 4 and 5 of the rubber damper portion is reduced, so that a margin for durability of the rubber dampers 4 and 5 is increased. You can also.

  Further, in the damper 1, since the pair of damper rubbers 4 and 5 also serve as a sealing function for the viscous fluid 16, it is necessary to provide a special part for sealing (such as the lid member 53 in the prior art in FIG. 4). There is no. Each component is obtained by combining two U-shaped parts 2 and 3 and inserting a part 7 having a rectangular section in the middle so as to be freely rotatable, and has an extremely compact shape as a whole. Therefore, it is possible to provide a damper product having a high attenuation and a compact structure.

Half cut sectional view of a viscous rubber damper according to an embodiment of the present invention Schematic diagram showing the configuration of the damper Graph showing the vibration damping characteristics of the damper (A) is a half cut sectional view of a damper according to a conventional example, and (B) is a schematic diagram thereof.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Viscous rubber damper 2 Hub 2a Boss part 2b Inner peripheral cylinder part 2c, 3b End surface part 2d Outer cylinder part 3 Rubber inertia mass 3a Small diameter cylinder part 3c Large diameter cylinder part 3d Pulley groove 4, 5 Damper rubber 6 Sealed space 7 Viscos Inertial mass 7a, 7c End face 7b Outer peripheral face 7d Inner peripheral face 8, 9, 10, 11 Minute gap 12, 13, 14, 15 Bearing 16 Viscous fluid a Rubber damper part b Viscous damper part c Crank system

Claims (1)

  By connecting a rubber inertia mass (3) to a hub (2) via a pair of damper rubbers (4) and (5), the hub (2), a pair of damper rubbers (4) and (5), and rubber inertia A sealed space (6) surrounded by the mass (3) is formed, and the viscous inertia mass (7) is rotatably incorporated into the sealed space (6), and the viscous inertia mass (7) and the hub (2) And a small gap (8) (9) (10) (11) between the viscous inertia mass (7) and the rubber inertia mass (3), respectively, and a viscous fluid ( A viscous rubber damper characterized by enclosing 16).

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