WO2000001956A1 - Anti-vibration apparatus - Google Patents
Anti-vibration apparatus Download PDFInfo
- Publication number
- WO2000001956A1 WO2000001956A1 PCT/GB1999/001264 GB9901264W WO0001956A1 WO 2000001956 A1 WO2000001956 A1 WO 2000001956A1 GB 9901264 W GB9901264 W GB 9901264W WO 0001956 A1 WO0001956 A1 WO 0001956A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- passageway
- walled
- vibrations
- rigid
- support means
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
Definitions
- the invention relates to a vibration damping arrangement, comprising an elongate
- passageway containing hydraulic fluid, means for causing the fluid to oscillate along the
- the invention also relates to an engine mount, for supporting the engine of a vehicle
- the enclosure including an
- the invention further relates to mounting apparatus for mounting part of the engine or transmission of a vehicle relative to the chassis or body thereof, comprising first and
- stiff resilient material extending between the two elements for relatively
- passageway being filled with hydraulic fluid which oscillates along the passageway in
- EP-A-0 012 638 There is shown an engine mount having a working chamber filled with
- fluid is pumped to and fro along the passageways by the flexing of a stiff rubber support which forms part of the wall of the working chamber and flexes with
- the passageways provide a resonant frequency for the
- fluid in the working chamber flows to and fro, according to the flexing of
- the passageway depends on various parameters including the dimensions of the passageway
- Anti- vibration apparatus in the form of hydroelastic mounts for mounting or limiting the
- Figure 1 is a cross-section through one of the engine mounts having a resonant conduit
- Figure 2 is a diagram for explaining the operation of the resonant conduit or passageway
- Figure 3 corresponds to Figure 1 but shows a modification
- Figure 4 corresponds to Figure 1 but shows a further modification
- Figure 5 is a cross-section through a modified form of a resonant conduit or passageway
- Figure 6 is a cross-section on the line VI- VI of Figure 7 through another of the engine
- Figure 7 is an underside view of the engine mount of Figure 5 but with some parts
- Figure 8 is a cross-section through a detail of another of the engine mounts
- Figure 9 is an end view of another of the engine mounts.
- Figure 10 is a cross-section through another form of the apparatus constructed as a
- the vibration damping apparatus of Figure 1 is in the form of an engine mount for mounting
- the engine of the vehicle supports the engine of the vehicle from the body or chassis of the vehicle.
- mount comprises a rigid metal bolt or pin 20 which use is in rigidly attached to the engine
- the engine mount incorporates a rigid metal
- the pin 20 is rigid with a metal bush 28 to which is bonded a cone-shaped rubber support 30 which defines a
- a rigid base plate 34 is sealingly attached to the turned-down edge 24
- Hole 36 connects with the interior of a flexible elongate resonator 38 comprises a
- the chamber 32 and the resonator 38 are filled with suitable hydraulic fluid.
- the rubber support 30 supports the static weight of the engine with respect to the body
- Such vibrations may be of low frequency and relatively large amplitude, such as
- the bellows turns 40,42,44,46,48 provide the resonator with correspondingly different
- resonator 38 acts on the fluid to cause damping at corresponding frequencies of vibration.
- a plate A is assumed to be vibrating to and fro in the direction of
- the vibrations of the plate A correspond to the vibrations of the engine in the engine
- the bellows turns are positioned and arranged so that they provide respectively
- the resonator 38 can be formed in a single piece by blow extrusion or blow injection.
- the operation of the resonator 38 can be adjusted to produce the required damping
- the wall defining the working chamber 32 is itself provided with a flexible
- the flexible wall 51 has a relatively large width portion 51 A which acts to
- a relatively lesser width portion 5 IB acts to provide dynamic damping at lower frequencies, such as corresponding to
- the resonator shown at 52 acts at still lower frequencies.
- the inertia of the fluid is a function of the square of its flow rate
- Figure 4 corresponds to Figure 3 and items corresponding to those in the preceding
- a resonator of in series with it, but acting in the same way at relatively high frequencies.
- Figure 5 shows how the resonator 53 in Figure 4 can be modified to provide a branched
- helical conduit 60 is connected to two bellows 62 and 63 at intervals along its length. These bellows are omitted from Figure 7 (but shown dotted there), and Figure 7 shows
- the fluid may vaporise or any gas bubbles
- Figure 8 shows a modification in which the flexible bellows in the passageway 39 of the
- Figure 9 shows another of the vibration damping arrangements but in an axi-symmetrical
- a rigid metal bush 65 is adapted to be rigidly connected to the engine, and
- an outer rigid metal circular casing 66 is adapted to be secured to the chassis or body of
- the bush 65 is bonded to a yoke
- the rubber yoke 67 defines diametrically
- Chambers 70,72 may be made of flexible plastics material. They are connected
- chambers 70,72 are filled with hydraulic liquid which also fills the passageway 74 and
- chassis or body to prevent undue movement of the engine in response to changes in
- Figure 10 shows vibration-damping arrangement in the form of a movement-limiter
- a central rigid metal boss 80 has a hole 82 by means of which
- Rubber stops 86 and 88 Rubber stops 86 and 88
- the rubber stops 86 and 88 are integrated in the chambers 98 and 100. They can be bonded to or simply in contact with the boss 80.
- Each rubber support 86,88 is enclosed within a respective flexible cover or bellows 94,96.
- the cover 94 defines a chamber 98 having an outer part 98A connected via bores 98B
- Cover 96 defines a similarly arranged
- Chambers 98 and 100 are filled with an hydraulic liquid which also fills
- parts 90 and 92 can be fixed to or part of the engine and the part 80 can be fixed
- the bellows 94,96 are less
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Combined Devices Of Dampers And Springs (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
Abstract
An engine mount for use in a vehicle comprises a pin (20) for connection to the engine and a support plate (22) for connection to the chassis or body of the vehicle. The support plate (22) defines an aperture with a turned-down edge (24). A stiff but resilient cone-shaped hollow support (30), made of rubber preferably, supports the engine from the support plate (22) and flexes in response to engine vibrations. The rubber support (30) defines a chamber (32) which is closed off by a base plate (34) but is open to a resonator (38), the chamber (32) and the resonator (38) being filled with hydraulic fluid. The resonator (38) comprises a longitudinally extending passageway (39) having a plurality of flexibly walled volumes (40, 42, 44, 46, 48) in the form of bellows turns which are positioned at respectively different predetermined positions along the length of the passageway (39) for providing the passageway (39) with correspondingly different resonant frequencies for the hydraulic fluid which oscillates along the passageway in response to engine vibrations. In this way, the resonator (38) causes damping at corresponding frequencies.
Description
ANTI- VIBRATION APPARATUS
The invention relates to a vibration damping arrangement, comprising an elongate
passageway containing hydraulic fluid, means for causing the fluid to oscillate along the
passageway in response to the vibrations, and means defining at least one flexible walled
volume open to the passageway to provide the passageway with a corresponding resonant
frequency for the fluid oscillating along the passageway whereby to damp or reduce the
transmission of the vibrations at that frequency.
The invention also relates to an engine mount, for supporting the engine of a vehicle
relative to the chassis or body of the vehicle and for damping vibrations of the engine
relative to the chassis or body, comprising a first rigid element for connection to the
engine, a second rigid element for connecting to the chassis or body, support means made
of stiff resilient material extending between the two elements for relatively supporting
them and flexing in response to the vibrations, and an enclosure partly defined by and
within the support means and filled with hydraulic fluid, the enclosure including an
elongate passageway along which the fluid oscillates in response to the vibrations and
having a resonant frequency dependent on the length of the passageway to cause damping
of the vibrations of that frequency.
The invention further relates to mounting apparatus for mounting part of the engine or
transmission of a vehicle relative to the chassis or body thereof, comprising first and
second rigid elements for respective connection to the said part of the engine or
transmission and to the chassis or body for relative vibration therewith, support means
comprising stiff resilient material extending between the two elements for relatively
supporting them and flexing alternately in first and second opposite directions in response
to the vibrations, means defining a first flexibly walled chamber mounted between the
support means and a first part of the first element so as to be compressed by flexing of the
support means in the first direction and to expand in response to flexing of the support
means in the second direction, means defining a second flexibly walled chamber mounted
between the support means and a second part of the first rigid element so as to be
compressed by flexing of the support means in the second direction and to expand in
response to flexing of the support means in the first direction, and an elongate
passageway between and interconnecting the two chambers, the two chambers and the
passageway being filled with hydraulic fluid which oscillates along the passageway in
response to the vibrations at a resonant frequency dependent on the length of the
passageway whereby to damp vibrations at that frequency.
Such arrangements, engine mounts and mounting apparatus are shown, for example, in
EP-A-0 012 638. There is shown an engine mount having a working chamber filled with
hydraulic fluid which also fills passageways leading from the working chamber to
terminate in flexible walled volumes in the form of thin- walled lateral chambers. In such
an engine mount, fluid is pumped to and fro along the passageways by the flexing of a
stiff rubber support which forms part of the wall of the working chamber and flexes with
the vibrations to be damped. The passageways provide a resonant frequency for the
oscillating fluid, the resilient frequency being dependent on various parameters including
the dimensions of each passageway.
Another such engine mount is shown, for example, in EP-A-0 277 056. In this known
arrangement, fluid in the working chamber flows to and fro, according to the flexing of
a rubber support forming part of the wall of the working chamber along an elongate tube¬
like passageway which extends away from the body of the engine mount to terminate in
a bulb having a flexible wall. Again, the resonant frequency for the oscillating fluid in
the passageway depends on various parameters including the dimensions of the
passageway.
According to the invention, the known form of arrangement as first set forth above is
characterised in that the flexible walled volume is positioned intermediate the ends of the
passageway between two relatively stiff-walled portions thereof.
According to the invention, the known form of first engine mount as first set forth above
is characterised by means defining at least one flexible-walled volume connected to the
passageway at a predetermined position along its length and between its ends to provide
the passageway with a predetermined resonant frequency for the oscillating fluid to cause
damping of the vibrations at that frequency.
According to the invention, the known form of mounting apparatus as first set forth above
is characterised by means defining at least one flexible walled volume connected to the
passageway at a predetermined position intermediate its ends to provide the passageway
with a corresponding further resonant frequency for the oscillating fluid to cause damping
of the vibrations at a corresponding frequency.
Anti- vibration apparatus, in the form of hydroelastic mounts for mounting or limiting the
movement of the engine or other part of a motor vehicle, and embodying the invention,
will now be described, by way of example only, with reference to the accompanying
diagrammatic drawings in which:
Figure 1 is a cross-section through one of the engine mounts having a resonant conduit
or passageway containing hydraulic fluid responsive to vibrations;
Figure 2 is a diagram for explaining the operation of the resonant conduit or passageway
of Figure 1;
Figure 3 corresponds to Figure 1 but shows a modification;
Figure 4 corresponds to Figure 1 but shows a further modification;
Figure 5 is a cross-section through a modified form of a resonant conduit or passageway;
Figure 6 is a cross-section on the line VI- VI of Figure 7 through another of the engine
mounts having a resonant conduit or passageway:
Figure 7 is an underside view of the engine mount of Figure 5 but with some parts
removed;
Figure 8 is a cross-section through a detail of another of the engine mounts;
Figure 9 is an end view of another of the engine mounts; and
Figure 10 is a cross-section through another form of the apparatus constructed as a
movement limiter.
The vibration damping apparatus of Figure 1 is in the form of an engine mount for
supporting the engine of the vehicle from the body or chassis of the vehicle. The engine
mount comprises a rigid metal bolt or pin 20 which use is in rigidly attached to the engine
by means of a suitable bracket. In addition, the engine mount incorporates a rigid metal
support plate 22 having an aperture with a turned-down edge 24 and holes 26 by means
of which the plate is bolted to the chassis or body of the vehicle. The pin 20 is rigid with
a metal bush 28 to which is bonded a cone-shaped rubber support 30 which defines a
hollow chamber 32 and whose generally circular base is bonded to the turned-down edge
24 of the plate 22. A rigid base plate 34 is sealingly attached to the turned-down edge 24
of the aperture in the plate 22 and closes off the chamber 32 except for a through hole 36.
Hole 36 connects with the interior of a flexible elongate resonator 38 comprises a
relatively stiff- walled passageway 39 interrupted by flexible walled volumes formed by
spaced flexible bellows turns 40,42,44,46,48 of progressively increasing diameter as
shown.
The chamber 32 and the resonator 38 are filled with suitable hydraulic fluid.
The rubber support 30 supports the static weight of the engine with respect to the body
or chassis of the vehicle and flexes resiliently in response to vibratory movements of the
engine. Such vibrations may be of low frequency and relatively large amplitude, such as
caused by movements of the engine as the vehicle is subjected to changes in the contour
or curvature of the road. Instead, they can be higher frequency and of lower amplitude
such as caused by the moving parts within the engine (e.g. when the engine is running at
idling speed).
In response to the vibrations, therefore, the flexing of the rubber support 30 produces a
pumping action on the hydraulic fluid which thus oscillates within the resonator 38 in
dependence on the frequency of the vibration.
The bellows turns 40,42,44,46,48 provide the resonator with correspondingly different
resonant frequencies for the oscillating fluid within the passageway 39. Accordingly, the
resonator 38 acts on the fluid to cause damping at corresponding frequencies of vibration.
The operation will be described in more detail with reference to Figure 2 which
illustrates, in diagrammatic form, the mechanical operations taking place within the
engine mount.
As shown in Figure 2, a plate A is assumed to be vibrating to and fro in the direction of
the arrows shown. The vibrations are transmitted by a spring B to a piston C acting on
hydraulic fluid within a chamber D.
The vibrations of the plate A correspond to the vibrations of the engine in the engine
mount of Figure 1. As already explained, these vibrations cause flexing of the rubber
support 30 (corresponding to the spring B in Figure 2), and produce a pumping action on
the fluid within the chamber 32 (corresponding to the action of the piston C on the fluid
in the chamber D of Figure 2). As shown in Figure 2, the fluid is thus pumped to and fro
along the passageway E which corresponds to the passageway 39 of resonator 38 of
Figure 1, except that the passageway E of Figure 2 is shown as only having two bellows
turns F and G instead of the several bellows turns of Figure 1.
When the vibrations have a relatively high frequency (and, generally, relatively low
amplitude), the to and fro movement of the hydraulic fluid within the passageway E takes
place along only a restricted part of its length indicated at H. The flexible bellows turns
F act at this frequency, causing the required damping.
However, at lower frequencies of vibration, when the vibrations have larger amplitude,
the to and fro movement of the fluid extends along the whole length of the passageway
E as shown by the arrow I, and the larger diameter bellows turns G come into operation
to produce the required damping.
At intermediate vibration frequencies, that is, between the high frequency vibrations
causing the fluid movement H and the low frequency vibrations causing the fluid
movement I, the fluid will move to and fro along respectively intermediate lengths of the
resonator and will be affected by the appropriate intermediate bellows turn shown in
Figure 1.
Therefore, the bellows turns are positioned and arranged so that they provide respectively
different resonant frequencies for the fluid oscillating in the passageway 39, thus
providing damping of the vibrations at these frequencies.
In order to protect the resonator 38 shown in Figure 1, it is desirable in practice to encase
it within a cover shown dotted at 50.
The resonator 38 can be formed in a single piece by blow extrusion or blow injection.
The operation of the resonator 38 can be adjusted to produce the required damping
characteristics by appropriate adjustment of various parameters:
(a) the ratio of the cross-section of the chamber 32 to the cross-section of the
passageway 39;
(b) the length of the passageway 39;
(c) by varying the cross-section of the passageway 39 along its length;
(d) by varying the number, position, size and flexibility of the bellows turns.
Items in Figure 3 corresponding to items in Figure 1 are similarly referenced.
In Figure 3, the wall defining the working chamber 32 is itself provided with a flexible
wall 51 which acts in the same way as the flexible bellows turns of the resonator 38 of
Figure I . The flexible wall 51 has a relatively large width portion 51 A which acts to
provide dynamic damping at relatively high frequencies. A relatively lesser width portion
5 IB acts to provide dynamic damping at lower frequencies, such as corresponding to
engine idling. The resonator shown at 52 acts at still lower frequencies.
In effect, for a certain rate of flow of the fluid caused by the pumping action of the rubber
support 30, the speed of the fluid flow depends on the cross-sectional area of each part
of the flow path. The inertia of the fluid is a function of the square of its flow rate, and
consequently a variation of the cross-sectional area produces a strong variation of the
inertia of the fluid.
Figure 4 corresponds to Figure 3 and items corresponding to those in the preceding
Figures are similarly referenced. In the arrangement shown in Figure 4, the resonator 53
has bellows arrangements 54 and 55 connected in parallel to the passageway 39, instead
of in series with it, but acting in the same way at relatively high frequencies. A resonator
56 acts at lower frequencies.
Figure 5 shows how the resonator 53 in Figure 4 can be modified to provide a branched
arrangement with two passageways 39A and 39B and a "Y" junction 57.
In Figures 6 and 7, items corresponding to those in other Figures are correspondingly
referenced. In Figure 6, the working chamber 32 is closed off by a plate 58 which is
apertured at 59 to connect with one end of a helical conduit 60 formed in a block 61. The
helical conduit 60 is connected to two bellows 62 and 63 at intervals along its length.
These bellows are omitted from Figure 7 (but shown dotted there), and Figure 7 shows
the shape of the conduit 60. When the vibrations have a relatively high frequency (and,
generally, relatively low amplitude), the to and fro movement of the hydraulic fluid along
the conduit 60 in response to the pumping action of the rubber support 30 takes place
along only a restricted part of its length. The flexible bellows turns 62 act at this
frequency, causing the required damping.
However, at lower frequencies of vibration, when the vibrations have larger amplitude,
the to and fro movement of the fluid extends along a greater length of the conduit 60, and
the larger diameter bellows turns 63 come into operation to produce the required
damping.
The arrangements shown in the various Figures can be used with advantage in engine
mounts (or similar supports) which are required to provide strong damping. In such
cases, particularly where the engine mounts are dimensionally small, very high pressure
variations can occur in the fluid. In such cases, the fluid may vaporise or any gas bubbles
entrained in the fluid may expand considerably, causing the support to act pneumatically
instead of hydraulically and thus with reduced damping. However, a resonator of the type
described can be used to provide two different resonant frequencies at which damping
occurs instead of only a single resonant frequency. One of the two resonant frequencies
is above and the other below the single resonant frequency. This enables the frequency
band for high damping to be enlarged without requiring a very high fluid pressure.
Figure 8 shows a modification in which the flexible bellows in the passageway 39 of the
engine mount of Figure 1 is replaced with a flexible membrane 64 to form a Helmotz
resonator.
Figure 9 shows another of the vibration damping arrangements but in an axi-symmetrical
form. Here, a rigid metal bush 65 is adapted to be rigidly connected to the engine, and
an outer rigid metal circular casing 66 is adapted to be secured to the chassis or body of
the vehicle, such as by an U-shaped clamp (not shown). The bush 65 is bonded to a yoke
made of stiff rubber 67 which extends radially outwardly in opposite directions and is
bonded to the inside surface of the casing 66. The rubber yoke 67 defines diametrically
opposite hollow spaces 68 and 69, each containing a flexible-walled hollow chamber
70,72. Chambers 70,72 may be made of flexible plastics material. They are connected
by a passageway 74 which incorporates flexible bellows arrangements 76 and 78. The
chambers 70,72 are filled with hydraulic liquid which also fills the passageway 74 and
the bellows arrangements 76,78.
When vibrations of the engine take place in the directions of the arrow shown in Figure
9, the bush 65 oscillates in these directions with reference to the casing 66, thus
compressing and expanding the chambers 70,72 alternately. The hydraulic fluid is thus
pumped to and fro between the two chambers at a corresponding frequency along the
passageway 74.
At low frequencies, damping is effected by the passage of the liquid along the complete
length of the passageway 74 from one chamber 70 or 72 to the other.
At higher frequencies, with lower amplitude vibrations, the fluid does not flow along the
full length of the passageway 74 between the two chambers. Instead, it flows from each
chamber to the adjacent flexible bellows arrangements 76,78 which produces the required
damping effect, in the manner explained with reference to Figures 1 to 7.
The arrangement shown in Figure 9 could instead be used as one end of an engine-
movement restraining link - for connecting a point on the engine to a point on the vehicle
chassis or body to prevent undue movement of the engine in response to changes in
engine torque.
Figure 10 shows vibration-damping arrangement in the form of a movement-limiter such
as for limiting movement of the engine of a vehicle relative to the chassis or body of the
vehicle, or for similarly limiting movement of some other part of the vehicle such as its
gearbox or transmission. A central rigid metal boss 80 has a hole 82 by means of which
it can be bolted to an arm 84 rigid with the engine or other part. Rubber stops 86 and 88
engage respective fixed parts 90 and 92 of an element rigid with the vehicle body or
chassis. The rubber stops 86 and 88 are integrated in the chambers 98 and 100. They can
be bonded to or simply in contact with the boss 80.
Each rubber support 86,88 is enclosed within a respective flexible cover or bellows 94,96.
The cover 94 defines a chamber 98 having an outer part 98A connected via bores 98B
through the rubber support 86 to an inner part 98C. Cover 96 defines a similarly arranged
chamber 100. Chambers 98 and 100 are filled with an hydraulic liquid which also fills
a passageway 102 extending through the boss 80 and a side channel 104 which terminates
in a flexible bellows 106.
Instead, parts 90 and 92 can be fixed to or part of the engine and the part 80 can be fixed
to the chassis or body of the vehicle. In such a configuration, the bellows 94,96 are less
subjected to the high temperature of the engine.
Vibration of the engine or other supported part in the direction of the arrows shown
causes resilient flexing of the rubber supports 86,88 and thus alternate compression and
expansion of the chambers 98 and 100. The hydraulic fluid is thus pumped to and fro
along the passageway 102, the movement of the fluid being damped by the bellows
arrangement 106 in the manner already explained.
Claims
1. A vibration damping arrangement, comprising an elongate passageway
(39,E,60,74,102) containing hydraulic fluid, means (30,67,86,8) for causing the fluid to
oscillate along the passageway (39,E,60,74,102) in response to the vibrations, and means
defining at least one flexible walled volume (40,42,44,46,F,51,54,55,62,63,64,76,78,106)
open to the passageway to provide the passageway with a corresponding resonant
frequency for the fluid oscillating along the passageway
(40,42,44,46,F,51 ,54,55,62,63,64,76,78, 106) whereby to damp or reduce the transmission
of the vibrations at that frequency, characterised in that the flexible walled volume
(40,42,44,46,F,51,54,55,62,63,64,76,78,106) is positioned intermediate the ends of the
passageway (39,E,60,74, 102) between two relatively stiff-walled portions thereof.
2. An arrangement according to claim 1, characterised in that the passageway
(39,E,60,74,102) is terminated in another flexible walled volume
(48,G, 52,56,63, 70,72,94,96) to provide the passageway with another corresponding
resonant frequency for the fluid oscillating along the passageway (39,E,60,74,102)
whereby to damp the vibrations at that frequency.
3. An arrangement according to claim 1 or 2, characterised in that there are at least
two of the flexible walled volumes (40,42,44,46,54,55,78,78) open to the passageway (39,E,60,74,102), at positions intermediate the ends of the passageway (39,E,60,74,102),
each volume being positioned at a respective predetermined position therealong to
provide the passageway (39,E,60,74,102) with correspondingly different resonant
frequencies for the fluid oscillating along the passageway whereby to damp the vibrations
at those frequencies.
4. An arrangement according to any preceding claim 1, characterised in that the
flexible walled volume (40,42,44,46,F,51,54,55,62,63,64,76,78,106) or at least one of the
flexible walled volumes (40,42,44,46,F,51,54,55,62,63, 64,76,78,106) comprises at least
one bellows turn.
5. An arrangement according to any one of claims 1 to 3, characterised in that the
flexible walled volume or at least one of the flexibly walled volumes comprises a flexible
membrane (64).
6. An arrangement according to any preceding claim, characterised in that the
passageway (39,E,60,74, 102) is relatively stiff-walled, and the or each volume
(40,42,44,46,F, 51,54,55,62,63,64,76,78,106) intermediate the ends of the passageway
(39,E,60,74, 102) interrupts the stiff walls of the passageway (39,E,60,74, 102).
7. An arrangement according to any one of claims 1 to 5, characterised in that the
passageway is relatively stiff- walled and the flexible walled volume (54, 106) or at least one of the volumes (54,106) intermediate the ends of the passageway
(40,42,44,46,F,51,54,55,62,63,64,76,78,106) is positioned in a respective stiff-walled
passage (39B,104) connected in parallel with the passageway (39,102).
8. An arrangement according to any preceding claim, characterised in that the
elongate passageway (60) is helical.
9. An arrangement according to any preceding claim for damping vibration between
two relatively vibratable rigid members, characterised by first and second rigid elements
(20,22;84,90,92) for respective connection to the rigid members to vibrate therewith and
stiff resilient support means (30,86,88) extending between the rigid elements
(20,22;84,90,92) and relatively supporting them and resiliently flexing in response to the
vibrations, the means for causing the fluid to oscillate along the passageway (39,102)
comprising means responsive to the flexing of the support means.
10. An arrangement according to claim 9, characterised in that the passageway forms
part of an enclosure (32,100) filled with the fluid.
11. An arrangement according to claim 10, characterised in that the enclosure is partly
defined by the support means (30,86,88).
12. An arrangement according to any one of claims 1 to 6, characterised by means defining two flexible-walled chambers (70,72,94,96) connected by the passageway, the
means for causing the fluid to oscillate along the passageway (74,102) in response to the
vibrations comprising means for respectively and altematingly compressing and
expanding the chambers (70,72,94,96) in response to the vibrations.
13. An arrangement according to claim 12, for damping vibration between two
relatively vibratable rigid member, comprising first and second rigid elements (66,65) for
respective connection to the rigid members to vibrate therewith, and support means (67)
made of stiff resilient material and extending from the second rigid element (65) to first
and second parts of the first rigid element (66) for relatively supporting the two elements
and resiliently flexing in first and second opposite directions in response to the vibrations,
one of the chambers (70) being mounted between the second rigid element (65) and the
first part of the first rigid element (66) so as to be compressed in response to vibration in
the first direction and expanded in response to vibration in the second direction, and the
other chamber (72) being mounted between the second rigid element (65) and the second
part of the first rigid element (66) so as to be compressed by vibration in the second
direction and expanded by vibration in the first direction.
14. An arrangement according to claim 13, characterised in that the first element
embraces an area including the second element.
15. An arrangement according to claim 14, characterised in that the first element (66) encircles the area and the second element (65) is mounted substantially at the centre of
the area so that the first and second directions extend oppositely along a diameter of the
area and the support means (67) extends radially and transverse to the diameter to define
two spaces positioned at opposite ends of the diameter in which are respectively located
the two chambers (70,72).
16. An arrangement according to claim 12, for damping vibration between two
relatively vibratable rigid members, characterised by first and second rigid elements
(90,92; 80) for respective connection to the rigid members to vibrate therewith, in that the
second element (80) is positioned between first and second spaced parts (90,92) of the
first element for movement in response to the vibrations towards each part in turn and
simultaneously away from the other, and by first and second support means (86,88) made
of stiff resilient material and respectively extending between the second rigid (80)
element and the first part (90) of the first rigid element and between the second rigid
element (80) and the second part (92) of the first rigid element for supporting the two
rigid elements (80,90,92) relative to each other and for resiliently flexing in response to
the vibrations.
17. An arrangement according to claim 16, characterised in that one chamber (98) is
defined between the second rigid element (80) and the first part (90) of the first rigid
element and the other chamber ( 100) is defined between the second rigid element (80) and
the second part (92) of the first rigid element.
18. An arrangement according to claim 17, characterised in that the chambers
(98,100) are respectively and at least partly defined by the respective support means
(86,88).
19. An arrangement according to any one of claims 16 to 18, characterised in that the
passageway (102) extends between the chambers through the second rigid element (80).
20. An engine mount, for supporting the engine of a vehicle relative to the chassis or
body of the vehicle and for damping vibrations of the engine relative to the chassis or
body, comprising a first rigid element (20,65) for connection to the engine, a second rigid
element (22,66) for connecting to the chassis or body, support means (30,67) made of stiff
resilient material extending between the two elements (20,65 ;22,66) for relatively
supporting them and flexing in response to the vibrations, and an enclosure (32,70,72)
partly defined by and within the support means (30,67) and filled with hydraulic fluid, the
enclosure including an elongate passageway (39,60,74) along which the fluid oscillates
in response to the vibrations and having a resonant frequency dependent on the length of
the passageway (39,60,74) to cause damping of the vibrations of that frequency,
characterised by means defining at least one flexible-walled volume
(40,42,44,45,54,55,60,62, 64,70,78) connected to the passageway (39,60,74) at a
predetermined position along its length and between its ends to provide the passageway
(39,60,74) with a predetermined resonant frequency for the oscillating fluid to cause
damping of the vibrations at that frequency.
21. An engine mount according to claim 20, characterised in that there are a plurality
of the flexible walled volumes (40,42,44,46,54,55,76,78) connected to the passageway
(39,74) at respectively different predetermined positions along its length and between its
ends for providing the passageway with corresponding different predetermined resonant
frequencies for the oscillating fluid to cause damping of the vibrations at corresponding
frequencies.
22. An engine mount according to claim 20 or 21 , characterised in that the passageway
(39,60,74) is relatively stiff-walled and the or each flexible walled volume
(40,42,44,46,54,55,60,62, 64,70,78) interrupts the stiff wall.
23. An engine mount according to claim 20 or 21 , characterised in that the passageway
(39,60) is relatively stiff- walled and the or each flexibly walled volume (54,62,63,64) is
positioned in a respective stiff-walled passage (39B) connected in parallel to the
passageway (39,60).
24. An engine mount according to any one of claims 20 to 23, characterised in that the
flexibly walled volume or one of the flexibly walled volumes is defined by a flexible
membrane (64).
25. An engine mount according to any one of claims 20 to 24, characterised in that the
passageway (60) is helical.
26. An engine mount according to any one of claims 20 to 25, a further flexibly walled
volume (48,56,70 or 72) which terminates the passageway.
27. An engine mount according to any one of claims 20 to 26, characterised in that the
or each flexibly walled volume (40,42,44,46,48,56,76,78) is defined by one or more
bellows turns.
28. An engine mount according to any one of claims 20 to 27, characterised by a
substantially rigid protective cover (50) enclosing the passageway (39).
29. Mounting apparatus for mounting part of the engine or transmission of a vehicle
relative to the chassis or body thereof, comprising first and second rigid elements
(66,65,90,92,80) for respective connection to the said part of the engine or transmission
and to the chassis or body for relative vibration therewith, support means (67,86,88)
comprising stiff resilient material extending between the two elements (66,65;90,92,80)
for relatively supporting them and flexing alternately in first and second opposite
directions in response to the vibrations, means defining a first flexibly walled chamber
(70,98) mounted between the support means (67,86,88) and a first part of the first element
(66,90,92) so as to be compressed by flexing of the support means (67,86,88) in the first
direction and to expand in response to flexing of the support means (67,86,88) in the
second direction, means defining a second flexibly walled chamber (72,100) mounted
between the support means (67,86,88) and a second part of the first rigid element (66,90,92) so as to be compressed by flexing of the support means (67,86,88) in the
second direction and to expand in response to flexing of the support means (67,86,88) in
the first direction, and an elongate passageway (74,102) between and interconnecting the
two chambers (70,72,98,100), the two chambers (70,72,98,100) and the passageway
(74,102) being filled with hydraulic fluid which oscillates along the passageway in
response to the vibrations at a resonant frequency dependent on the length of the
passageway (74,102) whereby to damp vibrations at that frequency, characterised by
means defining at least one flexible walled volume (76,78,106) connected to the
passageway (74,102) at a predetermined position intermediate its ends to provide the
passageway with a corresponding further resonant frequency for the oscillating fluid to
cause damping of the vibrations at a corresponding frequency.
30. Mounting apparatus according to claim 29, characterised in that the first rigid
element (66) is generally circular and the second rigid element (65) is mounted
substantially centrally thereof, the support means (67) extending radially in opposite
directions from the second rigid element (65) to the first rigid element (66) so that the first
and second directions extend oppositely along a diameter extending transverse to the
radial directions, the first and second parts of the first element (66) comprising portions
thereof positioned at opposite ends of the diameter, and the support means (67) defining
two spaces positioned at opposite end portions of the diameter, the two flexibly walled
chambers (70,72) being respectively mounted within the spaces.
31. Mounting apparatus according to claim 29, characterised in that there are at least
two of the flexibly walled volumes (76,78) connected to the passageway (74) intermediate
its ends, the flexibly walled volumes (76,78) being connected thereto at respectively
different predetermined positions along the length of the passageway (74) to provide the
passageway with correspondingly different resonant frequencies for the oscillating fluid
to cause damping of the vibrations at correspondingly different frequencies.
32. Apparatus according to claim 29, characterised in that the passageway (102)
extends through the second rigid element (80).
33. Apparatus according to any one of claims 29 to 32, characterised in that the or each
flexibly walled volume (76,78,106) is defined by one or more bellows turns.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB9814761.4 | 1998-07-07 | ||
GB9814761A GB2339259B (en) | 1998-07-07 | 1998-07-07 | Anti-vibration apparatus |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000001956A1 true WO2000001956A1 (en) | 2000-01-13 |
Family
ID=10835126
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/GB1999/001264 WO2000001956A1 (en) | 1998-07-07 | 1999-04-23 | Anti-vibration apparatus |
Country Status (2)
Country | Link |
---|---|
GB (1) | GB2339259B (en) |
WO (1) | WO2000001956A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3087240A1 (en) * | 2018-10-12 | 2020-04-17 | Psa Automobiles Sa | SHOCK ABSORBER HAVING AT LEAST ONE FLUID COLUMN COMPRISING FREE AND AUXILIARY INFLATION CHAMBERS |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3599955A (en) * | 1969-10-08 | 1971-08-17 | Gen Motors Corp | Nested composite spring assembly with multiple auxiliary spring units |
US4893797A (en) * | 1987-07-07 | 1990-01-16 | Automobiles Peugeot | Hydroelastic support, in particular for the suspension of a motor in a vehicle |
US4971300A (en) * | 1986-04-05 | 1990-11-20 | Firma Carl Freudenberg | Motor mount having improved hydraulic damping |
DE4119527A1 (en) * | 1990-06-18 | 1991-12-19 | Metzeler Gimetall Ag | Fluid filled damper for vehicle suspension - incorporates connection of working chamber to damping chambers |
US5193788A (en) * | 1991-03-04 | 1993-03-16 | Metzeler Gimetall Ag | Damping bearing assembly |
EP0822352A1 (en) * | 1996-07-29 | 1998-02-04 | Draftex Industries Limited | Vibration damping assemblies |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB811748A (en) * | 1956-07-31 | 1959-04-08 | Metalastik Ltd | Improvements in or relating to vibration dampers |
FR2349066A1 (en) * | 1976-04-20 | 1977-11-18 | Venissieux Atel | EFFORT DAMPER |
DE2962362D1 (en) * | 1978-12-07 | 1982-04-29 | Peugeot | Elastic mounting, particularly for the suspension of a vehicle motor |
DE3024092C2 (en) * | 1980-06-27 | 1984-12-06 | Boge Gmbh, 5208 Eitorf | Hydraulically damping single-chamber bearing |
FR2523246A1 (en) * | 1982-03-11 | 1983-09-16 | Dunlop Sa | PRESSURIZED FLUID DEVICES, SUCH AS ROLLS, SPRINGS AND / OR SHOCK AND / OR VIBRATION SHOCKS |
FR2609515B1 (en) * | 1987-01-14 | 1991-07-12 | Caoutchouc Manuf Plastique | ELASTIC ANTIVIBRATORY ISOLATION DEVICE WITH INTEGRATED HYDRAULIC DAMPING AND LIMITS FOR LIMITING INTERNAL TRAVEL |
DE3922744A1 (en) * | 1989-07-11 | 1991-01-24 | Sigma Laborzentrifugen Gmbh | VIBRATION DAMPER AND VIBRATED DAMPER CENTRIFUGE BEARING |
-
1998
- 1998-07-07 GB GB9814761A patent/GB2339259B/en not_active Expired - Fee Related
-
1999
- 1999-04-23 WO PCT/GB1999/001264 patent/WO2000001956A1/en active Application Filing
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3599955A (en) * | 1969-10-08 | 1971-08-17 | Gen Motors Corp | Nested composite spring assembly with multiple auxiliary spring units |
US4971300A (en) * | 1986-04-05 | 1990-11-20 | Firma Carl Freudenberg | Motor mount having improved hydraulic damping |
US4893797A (en) * | 1987-07-07 | 1990-01-16 | Automobiles Peugeot | Hydroelastic support, in particular for the suspension of a motor in a vehicle |
DE4119527A1 (en) * | 1990-06-18 | 1991-12-19 | Metzeler Gimetall Ag | Fluid filled damper for vehicle suspension - incorporates connection of working chamber to damping chambers |
US5193788A (en) * | 1991-03-04 | 1993-03-16 | Metzeler Gimetall Ag | Damping bearing assembly |
EP0822352A1 (en) * | 1996-07-29 | 1998-02-04 | Draftex Industries Limited | Vibration damping assemblies |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3087240A1 (en) * | 2018-10-12 | 2020-04-17 | Psa Automobiles Sa | SHOCK ABSORBER HAVING AT LEAST ONE FLUID COLUMN COMPRISING FREE AND AUXILIARY INFLATION CHAMBERS |
Also Published As
Publication number | Publication date |
---|---|
GB2339259A (en) | 2000-01-19 |
GB2339259B (en) | 2002-09-04 |
GB9814761D0 (en) | 1998-09-09 |
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