JPS60139938A - Hydraulic damping elastic bearing particularly for engine ofautomobile - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a three-elastic bearing for hydraulic damping, particularly for motor vehicle engines, comprising a ring-shaped rubber-elastic element, the rubber-elastic element surrounding a needle-shaped casing containing a damping fluid; and carrying a damping disk immersed in a damping liquid in a rigid connection part passing through the elastic element concentrically in an adhesive connection, and in a hydraulically damped elastic bearing, especially for motor vehicle engines, the ring a damping disk which is immersed in the damping liquid and has a rigid connection part which surrounds a needle-shaped casing containing a damping liquid and which extends concentrically through the elastic element in an adhesive bond; , in which the damping disk is axially movable and is guided in a form-constrained manner between an upper and a lower abutment surface.

In known bearings of this type (for example, DE 271 2 641 '), the damping disk is generally connected via an elastically deformable transmission element to a connecting part which directly accommodates the engine load. .

Such and likewise permanently active coupling between the damping disk and the connecting part results in, according to all practical experiments, the generation of a disturbing U-sound in the bearing.

For improved acoustic conditions of the bearing, it is desirable not to allow the damping disk to impact up to a certain limit amplitude of elastic movement and to give up any damping in this vibration range. The first task of the invention is therefore to create a free path in the damping disk in the lower range of the vibration amplitude, which is independent of the elastic movement of the bearing, to prevent the necessary acoustic coupling by each and at the same time to It is also to avoid the risk of sudden noise W1' caused by the generated load.

According to a first invention, the damping disk, which is guided in a radially constrained manner, i.e. without flexibility, provides the desired acoustic coupling, the elastic movement of the short culm length of the bearing being carried out in the liquid. Without the damping participation of the damping disk, the process proceeds uncontrolled and the ask only collides and is carried away after the selectable vibration amplitude has been exceeded. This type of □bearing meets the requirements generally placed on bearings. However, the bearing □ shows an unexpected disturbance in its damping characteristics under a given service, the cause of which is not recognized and is therefore determined purely empirically. Improved rt
The second problem of the present invention is to ensure that the unimpeded function of the damping device in elastic T-engine bearings increases the total vibration amplitude regardless of external conditions. The challenge is to make it safe through a rational process without discontinuities.

According to the invention, a first elastic bearing of the type mentioned at the outset is provided in which a damping disk made of a rigid material is located between the conically or spherically outwardly curved impact surfaces. Several grooves are provided at the connecting part so that it can move in the direction of the axis lJ - (°
In a first embodiment of the log invention, the damping disk is characterized by having overflow holes for the damping liquid in the area of the impact surface λ4, the damping disk is provided with a stepped screw screw screwed into the connecting part. According to an important sub-characteristic of the invention, the flow hole is a central hole receiving the shaft of the screw. is formed by four parts distributed at a constant angular pitch around the periphery and open in the direction of the bore, the head of the screw having substantially equal diameter as the cylindrical connecting part and facing its damping desk. The surface is formed into a conical or spherical shape in the same manner as the end surface of the connecting part.

The present invention solves the first set of problems in a surprisingly simple way. A damping disk guided form-constraintly in the shaft of the stepped screw without a flexible layer in the radial direction allows for limited axial movement clearance in both directions necessary for the intended acoustic coupling; There is also the possibility of varying the height of the free path and thus the range of the undamped amplitude, depending on the existing behavior or starting conditions, by adjusting the shoulder screw. However, risks such as collisions of the damping disk are solved on the other hand by the special form and arrangement of the through holes in conjunction with the conical or spherical form of the impact surface. In the cooperation of relatedly moved parts, fluid and compressive forces ensure that the direct recoil of the metal surface in the terminal phase of the free path is always and under all circumstances safely eliminated. The culm rises sharply, so that the vibration-damping T-1 abutments, known per se, with high bearing costs and large structural lengths can be dispensed with.

The second object of the invention is achieved, starting from a bearing of the type mentioned at the outset, by the use of a damping disc stabilized against cavitation according to the invention.

A new method to demonstrate the correctness of the method demonstrated by the present invention in practical research on bearings. If the saturated vapor pressure is achieved and then resolved again,
: This should be due to the uncontrolled sudden onset and resolution of steam blowing on the surface of the damping desk which is then refluxed. On the other hand, the removal of corrosive material from the surface as a direct result of this phenomenon has been considered unfavorable in the past, but no other measures are required to eliminate the impairment of the damping device due to cavitation loads. (j - It was hard.

The implementation of the inventive idea requires an influence on the flow process in the range of motion of the damping desk, the purpose of which is to
- To prevent the generation of negative pressure leading to saturated steam. Various measures can be used for this purpose, which are described in the embodiment section.

Embodiments of the present invention will be described based on the drawings.

First invention: The illustrated bearing is pressed into a brocade housing 2 with a fixing flange 21 made of steel plate, eave metal or other metal material, and is held in a shape-restricted manner therein, and at the same time a ring-shaped rubber elastic element 3 which also forms a closing part. The elastic element 3 is pierced over its entire length in the central direction by a metal connecting part 4, the mechanism being such that the connecting part 4 is fixed to the elastic element only in the upper region of the elastic element 3 and in the other regions. It is designed to be movable with a radial clearance over the longitudinal section. Housing 2 via a filling hole that can be closed by a plug 5
can today be filled with a high viscosity damping fluid 6.

In the installed state, the bearing is fixed by housing side flanges 21 to parts of the vehicle support structure (not shown); - the force-supported engine has a connection provided with a threaded hole 41 for receiving a fixing screw (not shown); Part 4 is placed directly on the soil, and the part mold is connected to the elastic element 3 through the connecting part.
It acts on F. In this way, pre-applied static loads are not taken into account in the context of the present application, since only the dynamic movement processes due to elasticity are important for the method of operation of the bearing within the scope of the invention.

In the figure, the lower inner end surface of the connecting part 4, which is immersed by the damping fluid 6, is inclined outwardly at a relatively small angle in the form of a truncated cone; The inner surface of the head 71 of the stepped screw 7 screwed into the external threaded hole 42 is also formed. A shoulder screw 7 serves for the attachment of the damping disk 8 to the connecting part 4; for this purpose the shoulder screw has a cylindrical shoulder 72 on the shaft part which connects directly to the head 71. The damping disk 8 is a flat circular shape made of a rigid material such as metal or cylindrical so as to be virtually undeformable, and has a cylindrical step portion 7.
A center hole d corresponding to or slightly larger than the outer diameter of 2.
, so that the damping disk is shown in FIG. 1 between the cone angles of parts 4 and 71, and is axially sliding and radially guided without play in the two-phase position. As is clear from FIG.
It is formed. However, the radial guidance of the step 72'' is not impaired.

The short-stroke elastic movement of the bearing takes place without damping due to the described axially movable mechanism of the damping disk without the involvement of the damping disk.

At the time of A, the desk is at rest in the damping liquid at the same time, and it is only after the predetermined vibration vibration exceeds 1'' that it is abutted by the connecting part A or by the head of the shoulder screw 7 and is moved 3F. .

In this case, the contact piece housing 11 is provided with both 'metal parts' 4/71.
A part passes through the four parts 81 and the outwardly conical pick-up surface and is damped in this case as a result of the constricted overflow of the damping fluid, so that no collision or impact noise occurs. do not have.

Second Invention 2' The bearing consists of a ring-shaped rubber elastic element 3 which also forms an I-shaped valve i with a bent fixed flange 21. The metal connecting part 4 is inserted into the elastic element 3 and fixed to it by adhesive in one region, and is radially attached to it by passing through the longitudinal part of the lower glaze of A. It is possible to exercise. The housing side 2 is filled with the damping fluid 6□ by filling the fill hole that allows the tr#1 chain to be filled with the stopper 5.

A mounted engine (not shown) is supported on a connecting part 4 which is provided with a threaded hole 41 for the attachment of fastening means.

12- The lower end surface of the fourth connection part, which is immersed in the damping liquid '6, slopes outwards in the form of a truncated pyramid and the screw thread 7 of the connection part
The inner surface of the head 71 of the stepped screw 7 screwed in at 1.42 is also formed into the same conical shape. The stepped screw 7 has a cylindrical stepped portion 12 extending over the head 71 for the purpose of attaching the thinning desk 8.

The configuration shown provides the damping disk 8 with limited axial movement possibilities between the conical surfaces of the sections 4 and 71. The f-recesses 81 provided in the holes of the damping disk allow a restricted overflow of the damping fluid.

In contrast to the bearing described for the first invention, the damping disk 8 according to FIGS. 2 and 2a has a large number of overflow holes for the damping fluid 6 distributed over its entire surface. It is equipped with 12. □ The overflow holes added in this fourth part 81 counter the flow □ The load peaks formed due to the rapid movement of the disk in the damping liquid on the surface of the disk are eliminated as soon as they occur or □ The damping blow The occurrence is reduced to the extent that it can be safely suppressed. For manufacturing reasons, it is recommended to form the flow holes 82 in radial continuity with a widening disk diameter and a widening inner diameter.

Similarly, the action without main capitalization is shown in Figures 3 and 3a.
A star-shaped damping disk 8 is obtained which is shown in the figure and is formed in the form of three equiangularly distributed circular segments around its circumference and is provided with a disk plane and twisted arms 83.

Another variation of the invention is shown in FIG.

In this case, the damping disk 8 is formed in a shape-constrained manner by six axially lined edges 84. The cross-sectional view shows the damping disk in its current installation orientation for the bearing shown in FIG.

[Brief explanation of drawings]

Fig. 1 is a longitudinal sectional view of a hydraulically damped elastic engine bearing of the first invention, Fig. 1a is a plan view of the damping disk of the bearing, and Fig. 2 is a hydraulically damped elastic engine bearing of the second invention. 2a is a plan view of a damping disk used in the bearing according to FIG. 2; FIG. 3 is a plan view of another embodiment of the damping disk; FIG. 3a is a plan view of a damping disk according to FIG. 3. FIG. 4 is a side view of the desk, and FIG. 4 is an axial cross-sectional view of another embodiment of the damping disk. Reference numeral 4 in the figure... Connecting part 6... Attenuation liquid 8... Attenuation desk 81... Engraving of Ezaki's prehistoric drawing as agent for overflow hole Mitsuyoshi Ezaki (no change in content) Fig. 1a Fig. 2 Fig. 20 Fig. 3 Fig. 83 Fig. 3a Fig. 4 September 1982, S-Japanese Patent Office Commissioner Kazuo Wakasugi, 1, Indication of the case Showa G patent application No. 241-(A'733 No. 2) , Title of the invention 3, Person making the amendment Relationship with the case Applicant 4, Agent 5, Date of amendment order March 71, 1939 6, Subject of amendment. 6 engravings of drawings. (No change in content)

Claims (1)

[Claims] (1) A liquid damping elastic bearing especially for an automobile engine, comprising a ring-shaped rubber elastic element, the rubber elastic element surrounding a needle-shaped casing containing damping liquid, In the case of a rigid connecting part (carrying a damping disk immersed in the damping liquid) extending concentrically in the adhesive connection, the damping disk (8) made of rigid material has a circular or round shape. It is attached to the connecting part (4) for axial movement between the spherically outwardly curved abutment surfaces and provides an overflow for the damping fluid (6) in the area of the abutment surfaces. Hole (
81) A hydraulically damped elastic bearing. (2) The shaft of a stepped screw (7), in which the damping disk (8) is guided in a form-constrained manner for axial movement on the shaft of the stepped screw (7), which is screwed into the connecting part (4). Claims 1 or 2 are formed as four parts distributed at angular distances in the phase N over the circumference of a concentric hole (d) containing and open to the hole (d). The sap damping valve described! 1 bearing. (4) The head (71) of the step E 1 screw (7) has a diameter approximately equal to that of the cylindrical connecting part (4), and the end face of the connecting part facing the damping disk (8) Hydraulically damped elastic bearing according to claim 2 or 3, which is formed conically or spherically in a similar manner. (5) Hydraulically damped elastic bearings, especially for motor vehicle engines, comprising a ring-shaped rubber elastic element, the rubber elastic element surrounding a needle-like casing containing damping fluid, and concentrically connecting the elastic elements in an adhesive connection. The rigid connection part with a through hole carries a damping disk that is immersed in the damping fluid, and the cocoon damping disk is movable in the axial direction between the upper and lower abutting surfaces. The damping disk (8) made of a rigid material is axially guided between the abutment surfaces which are curved outward in a circular or spherical manner. It is movably attached to the connecting part (4) and has overflow holes (81) for the damping fluid (6) in the area of the abutment surface.
), and a damping disk (18) stabilized against i-v vibration is used, in particular for a motor vehicle engine. (6) Hydraulic damping elasticity according to claim 5, wherein the damping disk (8) is formed by a large number of overflow holes (82) for the damping fluid (6) distributed over the entire surface of the disk. bearing. (7) Hydraulically damped elastic bearing according to claim 6, wherein the overflow hole (82) has an inner diameter increasing from the center in the direction of the outer circumference of the damping disk (8). (8) The damping disks (8) are formed by vane arms (83) which are equiangularly distributed over their circumference in a star-like manner and are formed in the manner of circular segments. Hydraulic pressure damping valve 1'l bearing as described in section. (9) Hydraulically damped elastic bearing according to claim 8, in which the vane arm (83) is twisted out of the plane of the damping disk (8). 10. Hydraulically damped elastic bearing according to claim 5, characterized in that the damping disk (8) is lock-shaped with a substantially axially bordered edge (84). (11) Hydraulically damped elastic bearing 1 according to claim 10, in which the edge ridge (84) of the damping disk (8) is edged by a dimension A-da which corresponds to several times the wall thickness. (12) Hydraulically damped elastic bearing according to claim 10 or 11, characterized in that the edge ridge (84) of the damping disk (8) is edged in the direction opposite to the elastic element (3).