Damped extended-motion strut

Abstract: A strut assembly (10) for providing a motion-damped tension and compression connection between a first object (10a, 10b) and a second object (12a, 12b) comprising: an elongate casing (10a, 10b) adapted to be disposed on an axis (A) extending between said objects (11a, 11b and 12a, 12b) a first member (16) mounted in said casing (10a) and adapted to be connected to said first objects (11a, 11b), a second member (17) movably mounted in said casing (10b) and adapted to be connected to said second object (12a, 12b), at least first member (16) being movable relative to said casing (10a, 10b), intermediate elastomeric means (22, 23) located in said casing (10a, 10b) between said members (16, 17) for limiting motion toward one another in the axial direction (A), terminal elastomeric means (20) located in said casing (10a, 10b) for limiting motion of said members (16, 17) away from one another in the axial direction (A), elastomeric means (20b) providing in said casing a deformable layer disposed alongside said axis, and ribbed means (25) in said casing (10a, 10b) in pressure engagement with said layer (20b) and responsive to motion of at least said first member (16) relative to said casing (10a, 10b) for slidably deforming said elastomeric layer (20b), whereby relative motion can be damped in opposite axial direction.

Description: The present invention relates to elements for providing a damped tension and compression connection between spaced objects, and more particularly the present invention relates to motion-damping torque struts such as find particular utility in vehicles to counter engine torque. In many front wheel drive automobiles currently on the market, the engine is mounted transversely in the engine compartment and is customarily supported on mounts and connected to a frame component of the automobile by means of a so-called torque strut. The torque strut functions to control angular displacement of the engine, such as when output torque increases during acceleration, and during braking, while accommodating normal engine oscillations, such as when the engine is operating at idle. Known torque struts include an elongate member mounting at opposite ends a pair of sleeved rubber bushings for receiving a connecting bolt. While such struts have been capable of performing the aforedescribed functions, they have certain limitations. For instance, the rubber bushings at the ends of the struts are prone to deterioration due to large motions across the bushings while subjected to the heat of the engine so that, after a period of time, the bushings crack and stiffen. As a result, the struts develop a proclivity for transmitting vibrations and noises to the frame and hence into the passenger compartment, particularly during acceleration of the automobile when the strut is subjected to substantial tensile loads. Special struts have been proposed to overcome some of the aforementioned problems. An example of such a strut may be found in US-A-4 392 640. The patented strut utilizes rubber bushings having specially shaped interior cavities for providing the desired motion accommodation. US-A-4 518 058 discloses a damped anti-torque strut which utilizes an hydraulic fluid displaceable axially in a chamber by means of a piston spring loaded into a central position. A strut representing an improvement over the aforementioned struts is disclosed in US-A-4 706 946 issued to Lord Corporation, the assignee of the present application. It incorporates friction elements to provide a friction damping action. This document shows the prior art as defined by the preamble of claim 1. Another type of mechanical connecting element useful for damping vibrations by utilizing elastomeric hysterisis and friction is disclosed in US-A-3 232 597 to Gaydecki. In Gaydecki, a ridged or corrugated member slides relative to an elastomeric layer to effect the desired motion damping. Several embodiments of motion damping connecting elements are disclosed. While the aforementioned struts may function satisfactorily for their intended purposes, there is a need for a durable and relatively low-cost torque strut which limits the transmission of engine vibrations over a broad range of engine operating conditions while being capable of readily being designed and manufactured to meet a wide variety of requirements. The present invention provides a novel strut assembly which is particularly suited for providing both a tension and a compression connection between relatively movable objects while simultaneously providing motion damping. The present invention also provides an improved torque strut which utilizes both friction and elastomeric hysteresis to provide the desired degree of motion damping. Alternatively the invention provides a unique torque strut which overcomes the limitations of knock torque struts by providing a desired amount of motion accommodation and damping without causing harsh snubbing action. In a further aspect the present invention provides a torque strut which is designed in such a manner as to enable different design requirements to be accommodated readily, which is reliable and rugged, and which can be manufactured efficiently utilizing known manufacturing technologies. More specifically, the present invention provides a strut assembly for use in forming a motion-damped tension and compression connection between first and second relatively movable objects. The strut assembly comprises an elongate casing which is adapted to be disposed on an axis extending between the objects. First and second axially-spaced members are mounted in the casing and are adapted to be connected to the first and second objects respectively. At least the first member is movable relative to the casing. Intermediate elastomeric means is provided between the members for limiting motion toward one another in the axial direction, and terminal elastomeric means is provided in the casing for limiting motion of the members away from one another in the axial direction. Frictional and hysteresis motion damping is provided by an elastomeric layer which is contained in the casing alongside the axis and which cooperates with ribbed means carried in the casing in pressure engagement with the layer. The ribbed means is displaced relative to the elastomeric layer in response to motion of at least the first member relative to the casing for slidably deforming said elastomeric layer whereby relative motion can be damped in opposite axial directions. In one preferred embodiment, a lost motion connection is provided between at least one of the members and its associated ribbed means for enabling the member to move a predetermined distance relative to the elastomeric layer without effecting a corresponding amount of motion of the ribbed means. The terminal elastomeric means is shaped to deform and provide energy absorption which increases with increased motion. The foregoing and other objects, features and advantages of the present invention should become apparent from the following description, when taken in conjunction with the accompanying drawings in which: Figure 1 is a plan view of a strut assembly embodying the present invention, the strut assembly being partially broken away and sectioned to illustrate interior details of construction; Figure 2 is a longitudinal sectional view taken on line 2-2 of Figure 1; Figure 3 is a view, similar to Figure 1, but illustrating a modified embodiment of the present invention; FIG. 4 is a longitudinal sectional view taken on line 4-4 of FIG. 3 but with portions of the outside of the casing shown in full; and FIG. 5 is a longitudinal sectional view of another embodiment of the present invention but with portions of the outside of the casing shown in full. Referring now to the drawing, FIG. 1 illustrates one embodiment of a strut assembly 10 constructed in accordance with the present invention. The strut assembly 10 is adapted to connect spaced relatively movable objects, such as the pair of spaced relatively movable brackets 11 a , 11 b and 12 a , 12 b . The strut assembly 10 is elongated on an axis A extending between the brackets 11 a , 11 b and 12 a , 12 b which may be components of a vehicle, such as an engine and a body or frame component. When thus installed, the strut assembly 10 can limit effectively the tendency of the engine to move relative to the vehicle by reacting either tensile or compressive forces applied on the axis A. To facilitate manufacturing by maximizing the use of identical parts, the strut assembly 10 comprises two substantially identical strut sections 10 a and 10 b which are joined together along a medial plane P orthogonal to the longitudinal axis A. The right-hand casing section 10 a comprises a formed metal shell 13 having a semicircular terminal strap-like end portion 13 a and a medial box-like portion 13 b defined by upturned and downturned pairs of flanges 13 c , 13 d , 13 e , 13 f , forming confronting channels joined along a horizontal plane. The flanges 13 e - 13 f are relieved adjacent opposite ends of the strut assembly at 13', 13" to provide mounting clearances. The companion strut section 10 b likewise includes a metal shell 14 which is shaped similar to the shell 13 but which has crimped flange portions 14 b embracing an outturned flanges 13 g of its companion shell 13 to form a secure transverse interlock along the medial plane P. In the illustrated embodiment, the shells 13 and 14 are rectangular in transverse cross section and have hollow elongate centrally located interior chambers C₁, C₂. The interlocked shell sections 13 and 14 cooperate to form a unitary strut casing 10 which, as will be described, can accept tensile forces applied on the axis A. For connecting the strut assembly 10 to the relatively-movable brackets, a pair of connecting members 16 and 17 are mounted in the casing chambers C₁, C₂ for movement relative to their respective strut sections 10 a and 10 b , and for movement relative to one another in the chambers C₁, C₂. In the illustrated embodiment, both connecting members 16 and 17 are of identical construction, but there may be installations which might require them to be different. The first connecting member 16 has a terminal lug end portion 16 e with a through bore 16' which is adapted to receive a fastener, such as the bolt 18, spanning across the member 16 and the brackets 11 a , 11 b . Preferably, spacers 19 and 20 (FIG. 1) are provided between the insides of the brackets 11 a and 11 b and the opposite sides of the connecting member 16 which, as best seen in FIG. 1, has a widthwise dimension which is less than the widthwise dimension of the casing chamber C₁ to facilitate assembly. The relief provided in the opposed flanges of the strut casing sections 10 a , 10 b provide a clearance for enabling the shell 13 to move axially relative to the brackets 11 a , 11 b . The companion, or second, connecting member 17 has a terminal lug end with a similar through bore 17' which is parallel to the bore 16' and which is connected by a bolt 21 and spacers 22 and 23 to the brackets 12 a , 12 b . When the strut sections 10 a , 10 b are square in cross-section, rather than rectangular, they may be arranged with the connecting bolt axes disposed at right angles to one another rather than parallel as shown. Since both sections 10 a and 10 b of the strut assembly are of like construction, further discussion will focus on the right hand connecting member 16 and associated structure, it being understood that the same comments apply to the left hand connecting member 17 and its associated structure. The right-hand connecting member 16 has a main body portion which is preferably of die cast metal, such as aluminum. The connecting member 16 has a rectangular recess 16 a which opens toward the medial plane P and which is defined by a continuous flange 16 b having a peripheral groove 16 c . The connecting member 16 has a pair of tapered surfaces 16 d , 16 d ,which converge toward the axis A from the region of the peripheral groove 16 c toward the lug portion 16 e in which the bore 16' is formed. The connecting member 16 is completely surrounded by a molded mass of elastomeric material 20 provided in the shell 13. The elastomeric material 20 has a terminal end portion 20 a which is recessed to receive the lug portion 16 e of the connecting member 16 and which has a box-like wall portion 20 b extending from the terminal end portion 20 a to the medial plane P. The wall portion 20 b surrounds the peripheral flange 16 b of the connecting member 16 in spaced relation. The elastomeric material 20 is shaped to engage the inner surface of the shell 13 and may be, and preferably is, bonded thereto. The terminal end portion 20 a of the elastomeric material 20 has a pair of protrusions 20 c , 20 c which project inwardly from the casing 13 transversely of the axis A to provide shoulders that engage the tapered surfaces 16 d , 16 d of the connecting member 16 in the manner illustrated in FIG. 2 when the strut assembly 10 is in its normal at-rest position. The terminal end portion 20 a of the elastomeric material 20 is suitably recessed around the lug 16 e in the manner illustrated to provide space for accommodating deflection of the protrusions 20 c , 20 c as the connecting member 16 moves axially rightward in use. The shouldered protrusions 20 c , 20 c of the elastomeric mass 20 engage the tapered surfaces 16 d , 16 d of the connecting member 16 over increasing areas as the connecting member 16 moves axially rightward, thereby created increasing frictional forces which aid in gently arresting axial rightward movement of the connecting member 16. Extreme rightward excursions of the connecting member 16 are completely arrested by an axial elastomeric abutment 20 d formed in the elastomeric mass 20 and located in the path of movement of the lug 16 e . In order to restrain axial inward motion of the connecting member 16, a block of elastomeric material 22 is provided in the casing chamber C₁. The elastomeric block 22 has a protrusion 22 a which is received within the recess 16 a of the connecting member 16 and a base 22 b extending outwardly from the protrusion 22 a across the ends of the connecting member flange 16 b . An identical block of elastomeric material 23 abuts the block 22 along the medial plane P and is similarly disposed with respect to the connecting member 17. Thus, the blocks 22 and 23 provide a centrally-located cushion which deforms in compression in response to axial inward motion of the connecting members 16 and 17, thereby absorbing energy imparted in that direction and limiting axial inward motion of the connecting members. For the purpose of damping motion of the connecting members, such as the connecting member 16 relative to its casing section 10 a , ribbed means is mounted in the chamber C₁ for movement relative to the elastomeric mass 20 in response to motion of the connecting member 16. In the embodiment illustrated in FIGS. 1 and 2, the ribbed means includes a collar-like slide element 25 carried on the connecting member 16 and mounted in its groove 16 c . Preferably, the ribbed slide element 25 has a plurality of contoured ribs, such as the pair of continuous, spaced, parallel, smoothly contoured ribs 25 a , 25 b formed in its outer periphery and disposed in pressure engagement with the elastomeric layer 20 b which surrounds it. Thus, when the slide element 25 is displaced in alternate directions by the connecting member 16 along the inside of the elastomeric wall 20 b , hysteresis develops within the elastomeric material of the wall 20 b to damp motion of the connecting element 16. Some energy is also dissipated due to frictional sliding motion of the slide element 25 along the wall 20 b . For a more detailed description of the theoretical underpinnings of this mechanism for providing motion damping, reference is made to US-A-3 232 597 to Gaydecki, the disclosure of which is incorporated by reference herein. The slide element 25 has a predetermined widthwise dimension, i.e. dimension parallel to the axis A. If desired, it may be dimensioned to completely occupy the axial extent of the groove 16 c in the connecting member 16, in which event it is directly coupled to the connecting member 16 so that all axial motion of the connecting member 16 causes the slide element 25 to move along the elastomeric layer 20 b . Also, because of the rectangular shape cocking motions of the member 16, such as vertically arcuate in FIG. 1 and horizontally arcuate in FIG. 2, result in damping of undesirable rotational motions in engine suspensions. There are many applications in which it is desirable to permit the connecting element 16 to move slight distances axially relative to the shell 13 without inducing friction or hysteresis damping. To this end, a lost motion connection is provided between the slide element 25 and the connecting member 16. In the embodiment illustrated in FIGS. 1 and 2, the lost motion connection is provided by causing the slide element 25 to have a slightly narrower widthwise dimension than the widthwise dimension of the groove 16 c and by causing it to have a coefficient of sliding friction relative to the connecting member 16 which is lower than the coefficient of sliding friction between it and its juxtaposed elastomeric layer 20 b . Typically, for automotive engine mounting applications, the widthwise dimension of the groove 16 c is in a range of about 0.254 to 2.032 mm (0.010 to 0.080 inches) greater than the widthwise dimension of the slide element 25. The material of which the slide element 25 is composed is important. It should have a ratio of static to dynamic, or sliding, coefficients of friction of approximately unity, with a relatively high coefficient relative to the elastomeric layer and a relatively low coefficient with respect to the material of which the connecting member 16 is composed. By way of example, polymeric compositions of reinforced nylon having up to about 20%, by weight, tetrafluoroethylene and about 2%, by weight of silicone lubricant additives are desirable for the slide element 25. Such a composition eliminates the need for a lubricant, such as a grease. For an engine mounting application, the coefficient of relative sliding friction between the ribbed outer surface 25 a , 25 b of the slide element 25 and its juxtaposed elastomeric layer 20 c should be in a range of about 0.2 to about 2.0, and the corresponding coefficient of relative sliding friction between the inner surface of the slide element 25 and the bottom of the groove 16 c of the connecting member 16 should be in a range of about 0.01 to about 0.1. Precompression of the elastomeric layer 20 c by the ribs 25 a , 25 b should be in a range of about 5% to about 30% of its thickness in the direction of applied compression. Assembly of the embodiment illustrated in FIGS. 1 and 2 is straightforward. Each strut section 10 a and 10 b is provided with the elastomeric material bonded therein. A slide element 25 is slid into place onto its associated connecting member by slipping it axially into its receiving groove from the lug end of the connecting member. Thereafter, the connecting members 16 and 17 are inserted, lug ends first, into their respective receiving chambers C₁, C₂. The elastomeric blocks 22 and 23 are then mounted in their receiving recesses in the connecting members 16 and 17 respectively, and the shells 13 and 14 are placed in a press in which their medial flanges are crimped together in the manner illustrated. The spacers 19 and 20 may be supplied with the strut assembly 10 and installed immediately prior to mounting between the brackets, or the spacers may be otherwise fastened to opposite sides of the connecting members after assembly as by welding, staking or adhesives. The above-described embodiment of the present invention provides several advantages. Included among these advantages are the fact that the stiffness of the strut assembly 10 in the tension and compression directions can be designed to be independent of one another. Variations in amplitude sensitivity and damping can be made by varying either the dimensional relations or the compositions of the materials of which the assembly is formed, or both. The metal components can be formed from strip steel utilizing conventional punch-press equipment, and the other components can be formed either by injection molding or die casting techniques. Another embodiment of the present invention is provided which affords certain manufacturing advantages, as well as the aforementioned functional advantages. Referring now to FIGS. 3 and 4, the modified strut assembly 110 is made from a single flat steel strip. The mating ends of sections 110 a and 110 b are joined together by a box-like metal coupling shell 130 which spans across the medial plane P and engages the outsides of the metal shells forming the strut assembly 110. The coupling shell 130 has a slot 130 a in its bottom wall which receives outturned tabs 113' and 114' provided on the shell portions 113 and 114 of the casing sections 110 a , 110 b , respectively. Assembly can be effected simply by sliding the casing shell axially inside the coupling shell 130 until tabs register with the slot whereupon they snap into place either with, or without, further steps such as spot welding, or peening. In order to provide motion damping, the coupling shell 130 is provided with vertically elongate lateral recesses 131, 132, 133, 134 (FIG. 3) in which are mounted correspondingly shaped elongate slide elements 125. In this embodiment, the slide elements are disposed with their ribbed surfaces 125 a , 125 b facing inward. See FIG. 3. A layer of elastomeric material 120 is molded around a solid wedge-shaped connecting member 116 which is adapted to be connected to a movable object, as by the bolt and bracket flanges illustrated. In this embodiment, the elastomeric material encases the connecting member 116 and provides an integral unitary structure for both the intermediate elastomeric means and the terminal elastomeric means as described in the embodiment of FIGS. 1 and 2. In this embodiment, the connecting member 116 has a pair of spacers 116 a and 116 b formed integral therewith. See FIG. 3. This embodiment functions in much the same manner as the embodiment of FIGS. 1 and 2 to damp motion; however, the stiffness of the strut assembly 110 can also be varied by adjusting the amount of elastomeric material filling the space surrounding the connecting members. As in the embodiment of FIGS. 1 and 2, a lost motion connection can be provided by properly dimensioning the slide elements 125 relative to their receiving recesses, and of course, adjusting the relative coefficients of sliding friction. In this embodiment, some cocking motions of the connecting members, i.e. arcuate up and down motions in FIGS. 3 and 4, can be accommodated as a result of the deflectability of the thin elastomeric sections 120 e on opposite sides of the connecting member. A further embodiment of the invention is provided which does not incorporate a lost motion connection. In this embodiment, 210, which is illustrated in FIG. 5, the ribbed means 225 is formed integral with each connecting member, such as the connecting member 216. While this construction is simpler and less expensive to manufacture, it does not afford the advantages of providing amplitude sensitive damping or of enabling damping characteristics to be changed readily by simple substitution of different slide element materials or configurations. In view of the foregoing, it should be apparent that the present invention now provides an improved strut assembly which overcomes the limitations of known strut assemblies yet which is rugged, reliable and straightforward to manufacture. While preferred embodiments of the present invention have been described in detail, various modifications, alterations and changes may be made without departing from the scope of the present invention as defined in claim 1.

Claims: A strut assembly (10) for providing a motion-damped tension and compression connection between a first object (11a, 11b) and a second object (12a, 12b) including: an elongate means (10a, 10b) adapted to be disposed on an axis (A) extending between said objects (11a, 11b and 12a, 12b), a first member (16) mounted in said means (10a) and adapted to be connected to said first object (11a, 11b), a second member (17) movably mounted in said means (10b) and adapted to be connected to said second object (12a, 12b), at least said first member (16) being movable relative to said means (10a, 10b), said assembly being characterized by said means being formed as a casing (10a, 10b), intermediate elastomeric means (22, 23) located in said casing (10a, 10b) between said members (16, 17) for limiting motion toward one another in the axial direction (A), terminal elastomeric means (20) located in said casing (10a, 10b) for limiting motion of said members (16, 17) away from one another in the axial direction (A), elastomeric means (20b) providing in said casing a deformable layer disposed alongside said axis, and ribbed means (25) in said casing (10a, 10b) in pressure engagement with said layer (20b) and responsive to motion of at least said first member (16) relative to said casing (10a, 10b) for slidably deforming said elastomeric layer (20b), whereby relative motion can be damped in opposite axial directions. A strut according to Claim 1, characterized by said deformable layer (20b) being disposed on the interior of said casing (10a, 10b) and said ribbed means (25) is carried on at least one of said first and second members (16, 17). A strut according to Claim 1 or Claim 2, characterized by said one of said members (216, 217) being of unitary construction and said ribbed means (225) is formed integral therewith. A strut assembly according to any one of the preceding Claims being characterized by means providing a lost motion connection between said one of said members (16, 17) and said ribbed means (25) for enabling said one of said members (16, 17) to move a predetermined distance relative to said layer (20b) without effecting a corresponding amount of motion of said ribbed means (25). A strut assembly according to Claim 4, being characterized by said lost motion means including a recess (131 - 134) in said one of said members (130) confronting said layer (120) and a ribbed slide element (125) mounted in said recess for sliding movement relative to said one member (130) through said predetermined distance. A strut assembly according to Claim 5, being characterized by said ribbed slide element (25) having a predetermined coefficient of sliding friction relative to said one member (16) which is lower than the coefficient of sliding friction relative to said layer (20b). A strut assembly according to Claim 1, characterized by said elastomeric means (20) being provided on at least one of said first and second members (116, 117) and said ribbed means (125) is provided on the inside of said casing (10a, 10b). A strut assembly according to any one of the preceding Claims, characterized by said terminal elastomeric means (20) including an elastomeric protrusion (20c) for engaging at least one of said members (16, 17) as it moves axially in said casing and deforming elastically to provide a spring-like energy absorption action. A strut assembly according to Claim 11, characterized by said elastomeric protrusion (20c) and said at least one member having surfaces that contact one another over increasing areas as said one member (16) moves axially. A strut assembly according to any one of the preceding Claims, characterized by said intermediate elastomeric means (22) including an elastomeric block (22) engaging said members and being compressible therebetween as said members move towards one another.

Inventors: THORN RICHARD P, THORN, RICHARD P.
Applicants: LORD CORP, LORD CORPORATION
Application year: 1990
Main classification: F16F13
IPC codes: B60K5, F16F13, F16F3, F16F7