FR2652626A1 - ELASTIC, CYLINDRICAL SUPPORT WITH FLUID FILLING HAVING EXCELLENT ISOLATION OR VIBRATION DAMPING CHARACTERISTICS. - Google Patents

Abstract

A resilient fluid-filled support comprising an inner sleeve and an outer sleeve (10, 12) an elastic body (14) interposed therebetween and defining at least in part a pressure-receiving chamber (36) filled with a fluid so that the pressure in this chamber varies due to the elastic deformation of the elastic body, an equilibrium chamber (50) filled with the fluid, and a calibrated passage (54) between the pressure receiving and equilibrium chambers . An enclosure (50, 52) is formed between the sleeves such that the enclosure is circumferentially spaced from the pressure receiving chamber, and a flexible partition (48) divides the enclosure into the equilibrium chamber and a chamber. of air (52) to allow the elastic deformation of the partition in order to absorb a variation in the pressure in the equilibrium chamber. A pressure controller (68, 70, 74, 76) is provided to change the pressure in the air chamber.

Description

The present invention relates generally to an elastic support

  cylindrical with fluid filling to absorb or isolate vibrations, based on the flows of an incompressible fluid contained in the support. More particularly, the present invention relates to such a fluid-filled elastic support which is of simple construction and which has excellent damping and / or insulation characteristics with regard to vibrations in a

wide frequency range.

  A cylindrical elastic support is known

  serving as a vibration damping device,

  terposed between two elements of a vibrating system, to flexibly connect these two elements. In this type of elastic support, an inner sleeve and an outer sleeve which are radially spaced from each other by a given radial distance are elastically connected by means of an elastic body interposed between them. The

  elastic support is intended to cushion or insulate the main

  mainly the vibrations which are received in a direction

  diameter of the sleeves. This type of support elas-

  cylindrical tick can be relatively compact and small, and it can be easily designed

  for a relatively reduced displacement value

  relative dial between the inner and outer sleeves

  when applying an excessive vibrating load.

  For these reasons, the cylindrical elastic support has been

  widely used as engine mount, differential mount-

  suspension and sleeving for automotive vehicles

biles.

  Recently, a so-called elastic support has been proposed.

  cylindrical fluid-filled tick having a plurality of fluid chambers which are defined between the inner and outer sleeves and which communicate with each other through a calibrated orifice, as described

  in Publications N 56-164242 and 63-289349 of request

  Japanese patents not examined. In this medium

  elastic with fluid filling, an incom-

  pressure filling the chambers with fluid is forced to flow between the chambers, through the calibrated passage, when a vibrating load is applied between the inner and outer sleeves. The elastic fluid-filled support isolates vibrations from Entrance,

  based on the flow of the mass of fluid through

  towards the calibrated pasasge, more efficiently than the sup-

  elastic wearing which only relies on the elasticity of the

  elastic body to absorb vibrations.

  However, in the elastic cylinder support

  fluid-filled plug of the type indicated above, an improvement in the vibration isolation function is obtained based on the resonance of the fluid, as regards only the vibrations whose frequencies are close to the frequency for which the calibrated pass is calculated. For example, the calibrated passage is determined to effectively dampen jerks and bounces of the motor and other low frequency vibrations, using fluid resonance. In this

  case, the calibrated passage works as if it were sensed

  closed only when the frequency of the vibration

  input is greater than the pitch tuning frequency

  wise calibrated. Therefore, the elastic support has

  a very high dynamic elasticity constant, i.e.

  say a very reduced effect of isolation or damping

  vibrations, with respect to the vibrations of

  high frequency yenne such as vibrations in

engine idling.

  In consideration of the above disadvantage of. cylindrical elastic support with fluid filling,

  it has been proposed to provide a control valve for or

  selectively screw and close the calibrated passage, in function

  tion of the type of input vibration, as described in

  Publication N 59-116 649 of a request for a model of utility

  Japanese unit not examined. The control valve is activated

  actuated by a suitable member, such as a solenoid, so that the calibrated passage opens and closes automatically to allow the elastic support to present

  different insulation or cushioning characteristics

vibrations.

  However, the use of the control valve

  for the calibrated passage leads to greater structural complexity of the elastic support due to the achievement of a fluid tightness at the location of the control valve and the installation of the actuator

  for the control valve. The manufacturing cost of the sup-

  elastic wearing is therefore greatly increased.

  The object of the present invention is therefore to provide a cylindrical elastic support with filling.

  of fluid which is of simple construction and which can

  fish or minimize the increase in the water constant

  dynamic elasticity with regard to vibrations whose frequencies are greater than the resonant frequency of the fluid passing through the calibrated passage, all

  at the same time having a sufficiently high effect of iso-

  vibrations based on the resonance of the fluid

crossing the calibrated passage.

  The above objective can be achieved in accordance with

  mement to the principle of the present invention which provides an elastic support filled with fluid to connect

  flexibly two organs, comprising: (i) a man-

  inner chon and an outer sleeve which are spaced from each other in their radial direction and to which are respectively fixed the two members to be connected in a flexible manner by the elastic support; (ii) an elastic body interposed between the inner sleeves and

  outside to elastically connect the inner sleeves

  laughing and external, the elastic body at least partially defining a pressure receiving chamber

  disposed between the inner and outer sleeves and rem-

  folds of an incompressible fluid, so that the pressure of the fluid in the depression-receiving chamber varies due to the elastic deformation of the elastic body during the application of a vibrating load between the inner and outer sleeves; (iii) means of

  definition of an enclosure which is arranged between the man-

  inside and outside and spaced from the bedroom

  receiving pressure in a circumferential direction-

  the inner and outer sleeves; (iv) a partition which comprises a flexible part and which divides the enclosure into a balance chamber of variable volume, filled with the incompressible fluid, and an air chamber for

  allow the flexible part of the partition to come off

  forming elastically in order to absorb a variation in the pressure of the fluid contained in the equilibrium chamber; (v) means for defining a calibrated passage for fluid communication between the pressure receiving chamber and the equilibrium chamber in order to allow the flow of fluid between these chambers; and (vi) pressure control means for changing the pressure

in the air chamber.

  The elastic support with fluid filling according to the present invention, constructed as described

  above, has a sufficiently large insulating effect

  vibration based on the resonance of the fluid

  pouring the calibrated passage when the pressure in the air chamber is adjusted to a relatively high value,

  for example when atmospheric pressure is applied

  as the air chamber. When the pressure in the air chamber is set to a relatively low value,

  for example by applying a reduced reduced pressure

  higher than atmospheric pressure in the air chamber, the elastic support has a constant of elasticity

sufficiently low dynamic range.

  Thus, by appropriate adjustment of the pressure control means, the present elastic support is capable of minimizing the increase in the dynamic elasticity constant with regard to the high frequency vibrations to which the calibrated passage does not act, while ensuring a high vibration isolation effect based on the resonance of the fluid passing through the calibrated passages, with respect to vibrations of relatively low frequency. Therefore, the present

  elastic support with fluid filling has ex-

  characteristic isolation or damping of vibrations in a relatively large range of the

vibration frequency.

  The pressure control means may include a vacuum source for providing reduced pressure below atmospheric pressure, and switching means which are connected to the vacuum source. The switching means can be operated between

  a first position, to apply the pressure at-

  air chamber, and a second position

  to apply the reduced pressure to the air chamber.

  The pressure control means can be connected to the air chamber via a suitable connector which is fixed to a hole made through a mounting bracket in which the outer sleeve is fixedly received. This hole communicates with the air chamber via a hole made through the outer sleeve. However, the connector can be fixed directly to the outer sleeve for the connection of the pressure control means to the

air chamber.

  In addition to the foregoing, the invention

  tion includes other provisions which stand out

  from the description which follows.

  The invention will be better understood using the

  additional description below, which refers to the

  attached sins in which: Figure 1 is an elevational view in cross section of a vehicle engine support according to the present invention; Figure 2 is a section along line 2-2 of Figure 1; Figure 3 is a cross section of an inner member of the engine mount of Figure 1, which is prepared by vulcanizing an elastic body between an inner sleeve and an intermediate sleeve: Figure 4 is a section along line 4- 4 of Figure 3; Figure 5 is a section through a first orifice definition part used in the engine mount of Figure 1; Figure 6 is a plan view of the first orifice definition part of Figure 5; Figure 7 is a section along line 7-7 of Figure 5; Figure 8 is a section through a second orifice definition part used in the engine mount of Figure 1; Figure 9 is a plan view of the second orifice definition part of Figure 8; and figure 10 is a section along the line

-10 of Figure 8.

  It should be understood, however, that these drawings and the corresponding descriptive parts

  are given only as an illustration of the ob-

  jet of the invention, which they in no way constitute

way a limitation.

  We first refer to Figures 1 and 2 which

  represent a cylindrical elastic support to be filled

  fluid fluid for a vehicle engine. On these figures

  res the reference 10 designates an inner sleeve of suitable metallic material. Radially outward: from this inner sleeve 10 is disposed an outer sleeve 12

  so that the two sleeves 10,12 are radially es-

  offset from one another eccentrically, with a dis-

  appropriate radial offset. Between the sleeves

  inside and outside 10,12 is interposed an elastic body

  tick 14 so as to elastically connect the two man-

  chons 10,12. The engine mount is installed on the vehicle, so that a vehicle engine assembly is attached to the outer sleeve 12 while the vehicle chassis is attached to the interior sleeve 10, the group

  motor thus being flexibly supported by the chassis

  located in the vehicle to absorb or isolate vibrations

  tions. The weight. of the engine group acting on the man-

  chcn outside 10 in the vertical direction in which-

  the the two sleeves 10,12 are mutually offset, the result is that the two sleeves 10,12 are held

  in substantially concentric or co-mutually related relationship

  xial. In this state, the motor support functions mainly to isolate the vibrations received in the direction of eccentricity of the two sleeves 10,12,

  i.e. in the vertical direction (as shown

  felt in Figure 1). This direction will be called

  "load receiving direction" where appropriate.

  An intermediate metal sleeve 16 having a relatively small thickness, more specifically

  described with reference to Figures 3 and 4, is arranged

  dialing outwards from the inner sleeve of the disc,

  which has a relatively high wall thickness. The man-

  interior and intermediate checks 10, 16, are mutual-

  eccentrically offset by an approximate radial offset distance

  requested in the direction of receiving charge. The man-

  inner and intermediate chons 10.16 are connected one

  to the other flexibly by the elastic body 14 in-

  terposed. As described below, the elastic body 14

  is formed by vulcanization so that the el-asti-

  that 14 is linked to the exterior and interior surfaces of the interior and intermediate sleeves 10, 14, respectively, in order to constitute an interior element as shown

in Figures 3 and 4.

  Between the intermediate sleeve 16 and the elastic body 14 is defined an axial cavity 18 formed in the axial direction of the support. As shown in Figures 1 and 4, the axial cavity 18 is located on one of the diametrically opposite sides of the inner sleeve 10, looking in the load receiving direction, for which the radial distance between the inner sleeves

  and intermediate 10.16 is smaller than this dis-

  tance on the other side. The axial cavity 18 has a substantially curved shape, seen in the plane of FIG. 3, which corresponds to approximately half of the circumference of the sleeves 10,16. Due to the presence of the axial cavity 18, the elastic body 14 exists only on said other side on which the above-mentioned radial distance is

  larger, i.e. only in the sensing part

  significantly higher than the inner space of the sleeve

  intermediate, as shown in figure 3. The cavity

  axial 18 does this to reduce or prevent a

  traction of the elastic body 14 due to the weight

  of the power unit acting on it by means of

  diary of the outer sleeve 12, when the mo-

  installed on the vehicle as described above.

  The elastic body 14 has a pocket 20 in the form of a recess opening into the outer circumferential surface, and the intermediate sleeve 16 has a window 22 aligned with the opening of the pocket 20, so that the pocket 20 is open to the outer surface of the intermediate sleeve 16. The pocket

  and window 22 are formed in respective parts

  tives of the elastic body 14 and the sleeve 16 which are so-

  killed opposite the axial cavity 18 in the direction

  diameter of the inner sleeve 10. More precisely, the pocket and the window 20, 22 are located on the side of the inner sleeve 10 o the offset distance

  inner and intermediate sleeves 10,16 is relative

  really big. The elastic body 14 is formed with a limiting rod 24 which passes through it in the direction

  axial of the motor support, so as to pass through the po-

  che 20. The opposite end portions of this rod

  limitation 24 are embedded and thus fixed in the pa-

  opposite lateral kings of the elastic body 14 which

  end the axial dimension of the pocket 20. The limiting rod 24 operates to protect said walls

  opposite side of the elastic body14 against deformation

  excessive displacement or movement in the axial direction

of the engine support.

  As shown in Figure 4, the sleeve

  intermediate 16 comprises an axially inter-

  middle 26 which is smaller in diameter than the other

  part. This axially intermediate part of more

  tit diameter 26 has a recessed region 28 over a circumferential length corresponding to that of

  the arc of the axial cavity 18, as shown in the figure

  gure 1. More specifically, the recessed region 28 is radially retracted inwardly relative to the rest of the axially intermediate portion 26, so that the bottom wall of the recessed region 28 cooperates with the elastic body 14 to define the axial cavity 18. Between the opposite ends of the recessed region 28 is formed a groove with partial circumference, the bottom of which is defined by the aforementioned remaining region

  of the axially intermediate part 26. Thus, the re-

  recessed gion 28 and partially circumferential throat

  tielle 30 together cover the total circumference of the

intermediate sleeve 16.

  The intermediate sleeve 26 of the element

  interior thus constructed, shown in Figures 3

  and 4, is subjected to a stretching operation to pre-compress

  sea elastic body 14 radially inward, as necessary. Next, a stop block 58 is placed in the pocket 20 and a first and second adjustment is made.

  32.34 hole definition pieces in the throat

  partially circumferential 30, as shown in FIG. 1. The first and second defining parts

  32.34 are substantially semi-finished parts

  cylindrical, as shown in Figures 5 and 8, respectively. The first orifice definition part

  32 covers half of the circumference of the sleeve

  intermediate 16 on the side of window 22, while the second orifice definition part 34 covers the other half, on the side of the recessed region 28. Next, we

  adjusts the outer sleeve 12 on the circumferential surfaces

  external annulars of the orifice definition parts 32, 34 and of the intermediate sleeve 16, and it is subjected to a stretching operation radially inwards. The external sleeve 12 comprises a layer of sealing rubber 56 formed on its inner circumferential surface, to ensure fluid tightness between the

  inner surface of the outer sleeve 12 and the surfaces

  these exterior orifice definition parts 32,34

and the intermediate sleeve 16.

  When the outer sleeve 12 is mounted on the inner element of Figures 3 and 4, the pocket 20 and the recessed region 28 are closed in a sealed manner

  fluid, so that a pressure receiving chamber

  sion 36 corresponding to the pocket 20 and an enclosure 50, 52 corresponding to the recessed region 28 are defined

  inside the engine mount. We fill the cham-

  pressure reception bre 36 with an improper fluid

  suitable sible. When applying a live charge

  brante between the inner and outer sleeves 10,12, the pressure of the fluid in the chamber 36 is modified by the elastic deformation of the elastic body 14 generated by the vibrating load. As indicated above, the stop block 58, of smaller dimension than the chamber 36, is movably housed in the chamber 36 so that the inner and outer sleeves 10,12 are protected against an excessive value of relative radial displacement

  by their stop contact with the stop block 58.

  As shown in Figures 5 to 7, the first

  first orifice definition part 32, arranged in a

  to close the pocket 22, has a spi-

  track 42 formed in the outer surface so that

  the inner end of the groove 42 is felt

  only in the center of the surface while the outer end is open at one of the opposite ends of the part 32, viewed in the circumferential direction of the motor support. The inner end of the spiral groove 42 communicates with a communication hole made through the wall thickness of the first

  orifice definition part 32. On the other hand, the second

  me orifice definition part 34, disposed on the side of the recessed region 28 of the intermediate sleeve 16,

  has two cutouts 44,44 at the circumferential ends

  opposite tials and two mutual rectangular windows

  slightly spaced 46.46 between the cutouts 44.44, as shown in FIGS. 8 to 10. This second orifice definition part 34 is provided with two elastically deformable or flexible membranes 48.48 fixed on its inner side in order to close windows 46.46

fluid tight.

  When the second part of the original definition

  fice 34 disposed between the intermediate sleeve 16 and the outer sleeve is in place, the aforementioned enclosure is divided by the flexible membranes 48,48, fixed to the part 34, in a variable volume equilibrium chamber 50, between the sleeve intermediate 16 and the membranes 48, 48, and two air chambers 52,52 between the membranes 48,48 and the outer sleeve 12. The equilibrium chamber

  is also filled with the incompressible fluid.

  Deformation or displacement of the membranes 48,48 com-

  thinks or absorbs a variation of the fluid pressure in the equilibrium chamber 50, and the air chambers 52, 52 have the function of allowing the deformation of the membranes 48, 48 when the fluid pressure in the

  balance chamber 50 varies. The description above

  shows that the membranes 48 constitute a partition which divides the aforementioned enclosure into a balance chamber 50

and in air chambers 52.

  When the first piece of original definition

  fice 32 is arranged between the intermediate sleeve 16 and the external sleeve 12, the spiral groove 42 is closed by the external sleeve 12 and it is maintained in fluid communication with the equilibrium chamber 50 by means of one of the cutouts 44 of the second

  orifice definition part 34 which is adjacent to the former

  outer end of the spiral groove 42. More pre-

  sharply, the pressure receiving chamber 36 and the balance chamber 50 are maintained in mutual communication by a calibrated passage 54 which is defined so that the spiral groove 42 communicating with the hole 40 and the cutout 44 is closed so fluid-tight by the sealing rubber layer 56 provided

on the outer sleeve 12.

  When applying a vibrating load in-

  be the inner and outer sleeves 10,12, the incompressible fluid is forced to flow between the pressure receiving chamber 36 and the equilibrium chamber, through the calibrated passage or orifice 54, due to a periodic variation pressure in the pressure receiving chamber 36, so that the vibration is damped, based on the resonance of the mass of

  fluid flowing in the calibrated passage 54. In the pre-

  feels embodiment, the passage calibrated 54 comp-

  the relatively long spiral groove 42

  large is tuned so that the resonant frequency

  that of the fluid flowing in the passage 54 is close to

  Hz, which falls within a vibration range of

  relatively low frequency, such as shaking of the mo-

  tor. This arrangement allows the engine mount to

  have an effective dynamic elastic constant-

  ment reduced with regard to low frequency vibrations.

  The incompressible fluid filling the cham-

  pressure and equilibrium reception vessels 36.50 can be water, an alkylene glycol, a polyalkylene glycol,

  silicone oil or a mixture of these substances.

  The filling of chambers 36.50 with the incom-

  pressure can be effected by mounting the outer sleeve

  laughing 12 on the inner element of Figures 3 and 4, in a mass of the selected incompressible fluid contained in

an appropriate tank.

  The engine support constructed and operating as described above is press fitted into a bore 60 formed in a fixing console 62, as shown in FIGS. 1 and 2. When the support

  engine is installed on a vehicle, the outer sleeve

  rieur 12 is fixed to the engine unit of the vehicle by the

  end of the fixing console 72, while a rod inserted through the inner sleeve 10 is fixed

* to the vehicle chassis.

  The fixing console 62 has two tapped holes 64,64 formed through respective parts of the cylindrical wall defining the bore 60, these

  parts being aligned with the two chambers respective-

  ves 52.52. These tapped holes 64,64 communicate with the respective air chambers 52,52 by respective holes 66,66 provided through the outer sleeve 12 and

the rubber layer 56.

  Two connectors 68,68 are screwed into the respective threaded holes 64, 64 and they are connected to

  respective air lines 70. Each hole ta-

  threaded 64 has a diameter larger than that of hole 66,

  so that an O-ring 72 arranged around the end

  outside open moth of hole 66 is held in con-

  pressure tact with the inner end face of the connector 68 and thus obtaining a fluid tightness between the outer surface of the outer sleeve 12 and the connector 68 to ensure a connection

  fluid-tight from air chamber 52 and pipe-

air space 70.

  The air pipes 70 communicating with the air chambers 52 via the connectors 68 are connected to a source of air pressure under

  the shape of a vacuum source 74 by means of

  mutation in the form of a switching valve 76. The switching valve 76 is electrically controlled

  so as to be selectively placed in a first po-

  sition, for the communication of the air chambers 52 with

  the atmosphere, and in a second position for the com-

  munication of the air chambers 52 with the vacuum source 64. When the air chambers 52 are open to

  the atmosphere via the switching valve

  tion 76, the air chambers 52 allow the flexible membranes 48 to deform freely and absorb

  thus a variation of the fluid pressure in the cham-

  balance bre 50. In this situation, the input load v brant applied between the inner and outer sleeves 10,12

  causes fluid to flow through the calibrated passage 54 due to a pressure difference between the pressure receiving and equilibrium chambers 36.50. Therefore, the engine mount has a sufficiently large damping effect in

  with regard to vibrations having a relative frequency

  tively low and a relatively large amplitude.

  When the air chambers 52 are connected to the vacuum source 74 by the air pipes 70 and the switching valve 76, on the other hand, the pressure in each air chamber 52 is lowered below atmospheric pressure , which tends to pull the membrane 48 towards the hole 66, so that the pressure in the

  equilibrium chamber 50 decreases correspondingly.

  In this situation, the engine mount does not have

  a sufficiently high damping or insulation effect

  input vibration load based on the resonant

  this of the mass of fluid flowing through the calibrated passage 54, but it has an elastic characteristic

  sufficiently flexible. More precisely, the elastic constant-

  dynamic ticity is reduced when the air chambers 52 are connected to the vacuum source 74. It appears

  that this reduction in the elastic constant dyna-

  The motor support is induced by a fluid absorption action from the equilibrium chamber 50 and a reduction in the resistance to the flow of fluid from the calibrated passage 54, which result from the reduction of

  the pressure in the equilibrium chamber 50.

  Thus, the present engine support is provided

  for controlling the switching valve 76 in operation

  tion of the vehicle's operating conditions so that the engine mount has different characteristics of

  operating to absorb or isolate effective-

  input vibrations. In particular, the regulation

  tion of the pressure in the air chambers 52 by the

  switching valve 76 and the vacuum source 74 is effi-

  cace to avoid the increase usually encountered in the dynamic elasticity constant when the motor support receives a vibrating load whose frequency is greater than that of the vibrations which can be

  sufficiently isolated by means of the resonance of the

  fluid mass through the cali- cal passage

  bré 54. For example, the switching valve 76 is brought to the first position to connect the air chambers 52 to the atmosphere when the engine support receives low frequency vibrations, such as a jolt.

  or a jerk of the engine, and we bring it to the second po-

  sition to connect the air chambers 52 to the source of

  empty 74 when the vehicle is stationary and the

  the engine idles. By control of the commu- nity valve

  tation 76 as described above, the engine mount not only has a high damping effect or

  of isolation with regard to tremors and to-

  engine blows, but also a low constant

  dynamic elasticity, that is to say an excellent

  isolation characteristic with respect to vibra-

  Idle positions with higher frequencies.

  The present engine support is however of relatively simple construction since the means of

  pressure control (64,66,68,70,72,74,76) for control

  der the pressure in the air chambers 52 in order to obtain the two different operating characteristics

  are arranged almost outside the engine mount.

  This is to be compared to the usual arrangement for opening and

  selectively close the calibrated passage, which is incorporated

  poré in the structure of the engine support. So,

  the present motor support can be of relatively large size

  tively small and manufactured at a reduced cost. Those are

  the advantages of this engine mount.

  In addition, the fluid tightness between the air pipes 70 and the air chambers 52 can be established by a simple connection of the connectors 68 to the tapped holes 64 of the fixing console 62, the seals

  O-rings 72 being clamped by and between the outer sleeve

  12 and connectors 68. Thus, the arrangement of

  tightness for connectors 68 and the fi-

  Attachment of connectors 68 are simple.

  Although the present invention has been described in its presently preferred embodiment, with a

  certain degree of particularity, by way of illustration only

  Lement, it is understood that the invention is not limited

  to the details of the illustrated embodiment.

  The numbers of press reception rooms

  Zion, balance and air 36, 50.52 are not limited to those of the illustrated embodiment. For example,

  the engine mount can include two air chambers

  pressure receptacle or more, and / or two pressure chambers

  balance or more. In addition, the engine mount can

  wear a single air chamber or three air chambers or

  plus, provided that each air chamber is selective-

  connected to the atmosphere and to the reduced pressure.

  The position of the air chambers 52 is not

  limited to that of the illustrated embodiment.

  For example, the equilibrium chamber (s)

  can be formed between the membrane (s) and the man-

  outside chon 12, while the air chamber (s)

  can be placed between the membrane (s) and the man-

intermediate chon 16.

  It is possible to modify, as appropriate, the

  truction and configuration of the calibrated passage 54, depending on the required insulation characteristics or

vibration damping.

  Although the fixing console 62 is provided in the illustrated embodiment, the console can be omitted. In this case, the air pipes 70 are connected directly to the outer sleeve 12 or

to the intermediate sleeve 16.

  Although the illustrated embodiment of the invention is used as an engine support for a motor vehicle, the principle of the present

  invention is also applicable to elastic supports

  fluid-filled ticks other than the engine mount, for example a differential mount and suspension sleeve for vehicles, and it is even applicable to vibration-damping / isolating components with fluid fill, such as as cylindrical dampers used for various devices or equipment other than those of motor vehicles.

  As is clear from the above, the information

  vention is in no way limited to those of its embodiments and of application which have just been described in a more explicit manner; on the contrary, it embraces all the variants which may come to the mind of the technician in the matter without departing from the framework or

  the scope of the present invention.

Claims (6)

  1.- Elastic fluid-filled support for flexibly connecting two members, comprising (a) an inner sleeve and an outer sleeve (10,12) which are spaced apart from each other in their straight direction   diale and to which the said two organs are fixed, res-   pectively, (b) an elastic body (14) interposed between said inner and outer sleeves, to elastically connect the inner and outer sleeves, said elastic body at least partially defining a pressure receiving chamber (36) disposed between said inner and outer sleeves and filled with an incompressible fluid, so that the pressure of said fluid in said pressure receiving chamber varies due to the elastic deformation of said elastic body when a vibrating load is applied between said inner and outer sleeves, and ( c) means for defining a variable volume equilibrium chamber (50), filled with said fluid, and a   calibrated passage (54) for fluid communication between   be said pressure and pressure receiving chambers   equilibrium in order to allow said fluid to flow between these chambers, characterized in that: an enclosure (50, 52) is defined between said inner and outer sleeves so that the enclosure is spaced from said pressure receiving chamber   in a circumferential direction of the inner sleeves laughing and outside;   a partition (48) comprising a flexible part   ble is provided to divide said enclosure into said variable volume balance chamber and into an air chamber (52) to allow said flexible portion to   said partition to deform elastically in order to absorb   ber a change in the pressure of said fluid in said equilibrium chamber; and pressure control means (68,70,74,76)   are provided to change the pressure in said air chamber.   2. Elastic fluid filling support according to claim 1, in which said pressure control means (68,70,74,76) comprise a   vacuum source (74) to provide reduced pressure   below atmospheric pressure, and switching means (76) which are connected to said vacuum source and which are movable between a first position, for communication of said air chamber (52) with   one atmosphere at atmospheric pressure, and a second   position for the communication of said air chamber with said reduced pressure.   3. Elastic fluid filling support according to claim 1 or 2, further comprising a   fixing console (62) in which said sleeve ex-   térieur (12) is fixedly received, and said sleeve ex-   with a communication hole with said   air chamber (42), said fixing console comprises   as a hole which communicates with said air chamber through said hole in the outer sleeve, the   said pressure control means comprising a pipe   an air line (70) connected to said hole in said fixing console to modify the pressure in said air chamber. 4. Elastic fluid-filled support according to claim 3, in which said air piping (70) is connected to said hole of said fixing console (62) by a connector (68) screwed into said hole in the mounting bracket.   5.- Elastic support with fluid filling   according to any one of claims 1 to 4, in   which said air chamber (52) consists of two mutually independent parts, said control means for   pressure being connected to the two said mutual parts- independent.   6.- Elastic support with fluid filling   according to any one of claims 1 to 5, in the-   which said calibrated passage (54) is defined by said outer sleeve (12) and by an orifice definition part (32, 34) disposed radially inward   of said outer sleeve and in contact with said sleeve   outer chon, said orifice definition part   comprising said partition (48) so that said partition   its extends inside said enclosure (50,52)   so as to cooperate with said defining part o-   hole to define said air chamber (52) 7.- Elastic support with fluid filling   according to any one of claims 1 to 6, comprising   further taking an intermediate sleeve (16) disposed between said elastic body and said outer sleeve (12), said intermediate sleeve having a region   recessed (28) which cooperates with said outer sleeve   laughing to define said enclosure (50,52).   8.- Elastic support with fluid filling   according to any one of claims 1 to 7, in   wherein said recessed region (28) and said partition (48) cooperate with each other to define said balance chamber (50).