Patent Description:
Many household appliances and other devices or machines use a suspension mounting between a vibration source such as a motor or pump and the rest of the device, to reduce vibration transmission, by isolating the vibrations from the rest of the device or damping the vibrations (i.e. dissipating their energy).

The aim is to avoid the vibrations being transferred to the outside of the device, e.g. the outer casing, which is undesirable. There is also a desire to avoid wear and noise through rattling. Certain noise components may also be particularly disturbing to users of an apparatus.

There are several known ways to reduce transmission of vibrations from a vibration source to the device housing. The most commonly used approach is a mass-spring mechanism, providing vibration reduction and vibration isolation (for example by making use of a <NUM> degree phase shift). Many different spring designs are known that provide vibration reduction and isolation. A wire coil spring is probably the most commonly used version. The spring may be formed as a compression spring, tension spring or torsion spring.

By way of example, a pump or motor may be mounted vertically on top of a compression spring. A pump or motor operated by the mains operates at <NUM> or <NUM> and this is accordingly the main frequency at which vibrations may arise. However, there are also many harmonics, at multiples of the base <NUM> or <NUM> level.

For vibration isolation based on use of a coil spring, a spring design is desired with a low spring constant and low amount of damping. A low amount of damping is desirable because this corresponds to a low dissipation of energy. A high damping, for example based on a spring combined with a viscoelastic material, means that part of the movement velocity of the component (e.g. pump or motor) is partially translated into deformation in the damping material as well as the deformation of the spring. Since the deformation expends a certain amount of energy, less energy is available for resonance. In many applications, the vibration reduction method is used to reduce the vibration amplitude at resonance.

For optimal vibration cancellation, energy dissipation via damping should be prevented, instead for optimal vibration cancellation, the vibration energy should be equal but opposite in direction with the rebound energy.

Standard compression, tension and torsion coil springs, have several disadvantages relating to the dynamics and acoustics.

<FIG> shows a compression coil spring in a relaxed state (left image) and in a compressed state (right two images). When vibrations are applied, the coils start to move and can touch each other as shown in the right two images in <FIG>. The coils at the ends can touch (middle image) or the middle coils can touch (right image). The coils may also rub or scrape along other device parts generating additional noise. In the middle section of the spring, this effect can be reduced by increasing the pitch, but at the ends (the start and end windings), this is often not possible. In addition, volume restrictions do not always allow such an increase in pitch.

The low spring constant of a coil spring is achieved by using multiple coils (so called "active coils"), that provide a large wire length compared to the thickness (L>>d). The low spring constant of the spring coupled to the component (motor or pump) mass results in a low system resonance frequency. Due to the relatively long but thin wire, the fundamental Eigen frequency (the first bending mode at the resonance frequency) of the spring itself is low as well. The result is a narrow effective operating range (frequency window) in which there is vibration reduction, free of resonances. This is illustrated in <FIG>, showing a plot of vibration transmission T (y-axis) as a function of angular speed ω (x-axis, rad/sec).

The value T is a measure of the amount of vibration found at the base (which should not vibrate) compared to the vibration of the vibration source. A value <NUM> indicates no difference between the base and the vibration source. A value ><NUM> means amplification at the base compared to the source (i.e. resonance). A value <<NUM> means vibration isolation.

Peak <NUM> is a resonance peak (i.e. resonant frequency) of the mass spring system at frequency fn_sys.

Crossing point <NUM> is at the frequency fn_sys * √<NUM>. This is the frequency at which vibration isolation starts.

Peak <NUM> is a resonance peak (i.e. resonant frequency) of the spring itself at frequency fn_local.

Crossing point <NUM> is at the frequency fn_local / √<NUM>. This is the frequency at which vibration isolation ends.

f_eff is the effective operating frequency window.

A coil spring consists of a long continuous curve with large radius of curvature, which does not provide additional rigidity for the wire against bending. The relatively long wire length is also not beneficial regarding optimal use of material and material cost. This length also means that the wire contains many local resonance modes, namely wire bending modes at specific frequencies, leading to reduced vibration isolation performance and other acoustic effects.

<CIT> and <CIT> each disclose motor mounts formed as bent wire arrangements. <CIT>, <CIT>, <CIT>, <CIT> and <CIT> disclose various components and damping reducing mountings.

There is therefore a need for an improved design for a vibration reducing mounting.

According to examples in accordance with an aspect of the invention, there is provided a system comprising:.

The weight of the component is transferred to the support plane through the first and second limbs.

This mounting makes use of a wire structure, forming an inner mounting portion and an outer support portion. This enables a structure with a low profile in that the outer support portion is around the inner mounting portion. The support plane of the outer support portion is parallel to the first plane of the mounting portion. As will be explained further down below, the bends enable the wire to have a relatively short length (e.g. compared to a multiple coil spring), and this means the local resonance modes are shifted to higher frequencies which increases the effective operating range for vibration isolation. The bends increase the local bending stiffness but maintain the overall spring constant of the mounting. Preferably, each of the bends of the first and second sequences has an angle of <NUM> degrees or less.

The term parallel is intended to cover minor deviations from parallel. For example, the term parallel may be taken to mean at an angle of <NUM> degrees or less.

The mounting may be formed as a single wire. The wire may for example be made of spring steel, and may have a diameter (or more generally a maximum linear dimension for example with a non-circular cross section) in the range of <NUM> to <NUM>, for example <NUM> to <NUM>, such as <NUM>.

Note that there may be a bend between the mounting portion and the first first limb section and between the mounting portion and the first second limb section. These bends occur before the defined sequences of bends and thus do not form part of said sequences. Similarly, bends leading to the first and second limb mounting portions occur after the defined sequences of bends and thus do not form part of said sequences.

The sequences of bends are located in a section of the mounting between the mounting portion and the support plane.

The first and second planes may be offset from each other.

The offset between the first and second planes is caused by the sequences of bends, and it means bending stiffness is provided in more than one plane.

The mounting portion may comprise an open loop, the ends of the open loop defining the one end and the opposite end of the mounting portion.

The open loop may for example be clipped around a channel of the component to be mounted. This may be achieved by flexing open the open part of the loop, fitting the loop around the channel, and allowing the loop to close around the channel. This provides an easy to fit structure, in the form of a spring clip.

By "open loop ring" is meant a loop which extends around at least <NUM> degrees, preferably around at least <NUM> degrees, for example <NUM> degrees or more. Thus, the loop ring formed by the single wire may be used to grip around a circumferential portion of the component and thereby retain it in position within the plane, and the mounting structure provides damping perpendicular to the plane.

The first limb mounting portion and the second limb mounting portion may each comprise a hook. Each hook for example comprises a wire portion after a <NUM> degree bend. The hooks can be fitted into receiving portions of a support structure which is to support the component to be mounted.

Each of the bends in the sequences of bends may have a bend radius less than or equal to <NUM> times the diameter (or more generally maximum dimension in cross section) of the wire.

The bends are thus tight bends rather than gradual curvature in the wire. These sharp bends increase the bending stiffness.

The one end of the mounting portion is for example at one side of the mounting portion, and the other end of the mounting portion is at an opposite side of the mounting portion, wherein the mounting portion is side-side symmetrical. Thus, the limbs extend outwardly from opposite sides of the mounting portion. The overall structure may be side-side symmetrical.

The last first limb section and the last second limb section may be at an angle of less than <NUM> degrees to each other. Thus, they form two parallel or near parallel lines on opposite sides of the mounting portion, and thereby form a balanced support structure.

The last first limb section and the last second limb section may each have a length greater than the maximum linear dimension of the mounting portion. The support plane as defined by the last first limb section and the last second limb section can thus extend over a large area, extending beyond the projection of the mounting portion. Such support plane may provide vibration reduction of off-axis vibrations as well as axial vibration (wherein the axis may be defined as perpendicular to the first and second planes).

In a first example, the first and second sequences each comprise exactly two bends and wherein the first first limb section and the first second limb section are collinear and extend outwardly from opposite sides of the mounting portion.

This is one example, with a minimum number of bends to achieve an offset between the first and second planes.

In a second example, the first and second sequences each comprise exactly four bends, wherein the first first limb section and the last first limb section are at an angle of between <NUM> and <NUM> degrees and wherein the first second limb section and the last second limb section are at an angle of between <NUM> and <NUM> degrees.

This is another example, in which the bends form a generally U-shaped structure for each limb. The first first limb section and the first second limb section may for example be parallel and side by side and lie in the first plane.

The vibration inducing component is for example mounted vertically and the first plane and the second plane are horizontal. The vibration inducing component may comprise a pump or motor.

The invention also provides a coffee machine comprising:.

The invention provides a vibration reducing mounting comprising a wire which follows a path which comprises a mounting portion for fixing to a component to be mounted in a first plane and first and second limbs extending outwardly from the mounting portion. Each limb has a sequence of bends and the end sections lie in a second plane parallel with the first plane and which functions as a support plane. The end sections extend across opposite sides of the mounting portion. At least one of the bends and preferably each bend of the bend sequences has an angle of <NUM> degrees or less.

Before describing the various mounting designs, investigations which were carried out and which culminated in the designs of the invention, will first be explained.

<FIG> shows how the required wire length (x-axis, mm) depends on the wire diameter (y-axis, mm) to achieve a given spring constant (here: 10kN/m) for different designs (here: straight or coiled, coil number, coil diameter). Plot <NUM> is for a straight wire. Plot <NUM> is for a coil spring having a single coil and plot <NUM> is for a coil spring having five coils. The different points in the respective plots <NUM>, <NUM> correspond to different coil diameters. Plot <NUM> is for a coil spring and the different points correspond to different numbers of coils.

<FIG> thus generally shows that, for a given fixed spring constant (in this case 10kN/m), a straight wire requires (in most cases) much smaller wire length than different variants of coil-shaped wire springs. Generally, the shorter the free (unsupported) wire length, the higher the local or first natural bending mode frequency fn_local. The shorter length would therefore be preferred since the shorter unsupported wire length would normally also result in a higher first natural bending frequency fn_local (cf. peak <NUM> in <FIG>).

However, wire length is not the only discriminating factor regarding the frequency fn_local, since wire thickness also plays an important role.

<FIG> shows the first natural frequency fn_local (y-axis, Hz) of a spring wire depending on the spring design. The x-axis shows the required wire volume (m<NUM>).

Plot <NUM> is for a straight wire spring, simply supported at both ends, to achieve a spring constant of 1kN/m. The overlapping plots <NUM> are for different coil spring designs and a straight wire design to achieve a spring constant of 10kN/m. The area <NUM> is for the straight wire design.

The overlapping plots <NUM> for k=10kN/m and the region <NUM> show that a straight wire spring design indeed enables the spring volume requirement to be lower than for a coil spring design. The straight wire spring design provides a higher local bending mode frequency fn_local (cf. peak <NUM> in <FIG>).

However, a large part of the straight wire plot overlaps with the volume requirements (and thus fn_local) of a coil spring shape, meaning that there is a limited benefit for a straight wire spring design to achieve a given spring constant.

Plot <NUM> shows that the resonance frequencies can be influenced by changing the spring constant (k=10kN/m for all other plots) to a different value (k=1kN/m).

In order to shift the first resonance frequency of the spring itself, the invention makes use of sharp bends along the length of the wire. This provides segmentation of the wire into segments between the bends, and the local bending frequency fn_local, can be increased dramatically.

Plot <NUM> shows the results for examples of wires with <NUM> and <NUM> bends, simply supported at both ends.

<FIG> shows these wire designs. The top image shows a straight wire, the middle image shows a wire with one bend in the middle with angle α and angle β at the two simply supported ends, and the bottom image shows a wire with two bends in the middle each with angle α, and angle β at the two simply supported ends. The two bend angles α do not have to be equal. The bend angle β is with reference to the horizontal. The horizontal distance between the two support points may be considered to be an effective length L_eff.

<FIG> shows a plot of the first natural frequency fn_local (y-axis, Hz, logarithmic scale) i.e. the peak <NUM> in <FIG> versus the bend angle α (x-axis, degrees) for a fixed effective wire length and diameter. Plot <NUM> is for one bend and plot <NUM> is for two bends (wire diameter <NUM>, length <NUM>).

<FIG> shows that the smaller the bend angle α, the higher the first resonance frequency fn_local becomes. The required bend angle α is dependent on the number of bends, but roughly ≤<NUM>° for a number n of bends n=<NUM> and n=<NUM> in these examples.

To simplify further, <FIG> shows the effect of plotting the data from <FIG>, but with the ratio L_effective / L_wire (as the x-axis, dimensionless) instead of the bend angles.

The point <NUM> is a reference with no bend. The first resonance frequency fn_local increases as the ratio is reduced. The lines now plot on top of each other, meaning that the ratio L_effective / L_wire determines the amount of shift of the first natural frequency fn_local of the spring wire itself. By way of example, to obtain <NUM>% shift of fn_local, the ratio L_effective / L_wire needs to be reduced to approximately <NUM>%.

To obtain a substantial benefit regarding the acoustics and dynamics, a shift of ≥<NUM>% in the value of fn_local would be preferred, meaning that the ratio L_effective / L_wire should be reduced to around at most <NUM>% of the value for a straight wire.

The increase in resonance frequency fn_local is valid for a vertical bending direction as shown in <FIG>. For multiple bends, the bends will be in multiple directions.

<FIG> shows a first example of a design for a vibration reducing mounting which has been developed based on the findings explained above.

The vibration reducing mounting <NUM> comprises a wire <NUM>, which follows a path which comprises a mounting portion MP for fixing to a component to be mounted in a first plane and first L1 and second L2 limbs extending outwardly from the mounting portion. Each limb L1, L2 has a sequence of bends. In this example, there are four bends in each limb (after the first bend leading out from the mounting portion and before the final bend leading to a hook at the end of the wire). The end sections L1END and L2END lie in a second plane parallel with the first plane and which functions as a support plane. The end sections extend across opposite sides of the mounting portion. Each of the bends of the bend sequences has an angle of <NUM> degrees or less. In this example the bends are all in the range <NUM> to <NUM> degrees.

Note that the planes of the mounting portion MP and the end sections are intended to be parallel when the mounting <NUM> is in a loaded condition, i.e. when the mounting portion is supporting the vibrating component.

Before supporting the vibrating component, the mounting portion may be non-parallel with the plane of the end portions (which may be considered to be a support plane). For example, with reference to <FIG>, the top right part of the loop forming the mounting portion (i.e. opposite the opening in the loop) may be elevated. Only when supporting the mass of the vibrating component will the mounting portion bend down against the spring bias of the wire to bring the plane of the mounting portion parallel or near parallel with the support plane.

Thus, the planes are parallel in use, by which is meant when the mounting <NUM> is in a loaded state. In the unloaded state, there may be an angle of <NUM> to <NUM> degrees between the plane of the mounting portion and the support plane.

The mounting <NUM> has no wire parts close to each other, which prevents rattling or scratching noises. The wire <NUM> generally has the mounting portion MP in one plane and both ends in another plane (rather than one end at the top and one end at the bottom as is the case for a coil spring).

In the example shown, each limb L1, L2 defines a <NUM> degree path from its exit direction from the mounting portion MP to the end of the limb. In an alternative embodiment (not shown) the path of each limb may define at most <NUM> degrees from the exit from the mounting portion to the end of the limb (in which case the limbs together form one circle around the mounting portion). Thus, the limbs together define at most one circuit around the mounting portion.

In <FIG>, the mounting portion MP comprises a ring for supporting or attachment to the vibration source, and its plane is at a different height compared to the support plane defined by the end sections L1END and L2END. This requires that some bends (e.g. bends B1 and B2, see <FIG>) are not in the same plane as the other bends. An advantage of this is that it provides bending stiffness in other planes, other than only in the horizontal plane.

Corresponding pairs of limb sections for example each lie in a respective plane, and the planes for the pairs of limb sections are not then parallel with the support plane and the plane of the mounting portion. Thus, third and further planes may be considered to be defined by the structure.

In the simpler alternative of a planar structure (i.e. the first and second planes are the same plane) the wire would be able to bend easily into the orthogonal plane. This may or may not be desirable, depending on the nature of the vibrations to be isolated. An offset between the two planes is in most cases preferred but it is not essential.

<FIG> is used to explain the structure in more detail, in particular the limbs are referenced in more detail. The first limb L1 comprises a first sequence of bends B1 to B4 between a first first limb section L1SFIRST and a last first limb section L1SLAST (corresponding to L1END in <FIG>), and a first limb mounting portion L1H at the end of the last first limb section L1SLAST.

Note the reference LxSy denotes limb number x (<NUM> or <NUM>) and section number y (first through to last) for that limb. The notation "nth mth limb section" denotes the nth section of the mth limb.

The second limb L2 comprises a second sequence of bends between a first second limb section L2SFIRST and a last second limb section L2SLAST (corresponding to L2END in <FIG>), and a second limb mounting portion L2H at the end of the last second limb section L2SLAST.

Because there are four bends, there are five sections in total, i.e. three more (L1S2, L1S3, L1S4 for the first limb and L2S2, L2S3, L2S4 for the second limb) between the first and last sections.

The last limb sections L1SLAST and L2SLAST extend across opposite sides of the mounting portion MP. Thus they form a cradle structure on both sides of the mounting portion MP. At least one bend and preferably each bend is sufficiently tight (with an angle of <NUM> degrees or less, preferably <NUM> degrees or less) to influence the rigidity of the structure.

The offset between the first and second plane is for example in the range <NUM>% to <NUM>% of the maximum linear dimension of the mounting.

As shown in <FIG>, the mounting portion MP comprises an open loop, wherein the ends of the open loop define one end and an opposite end of the mounting portion. The limbs L1, L2 may be pulled apart to open the loop further so that it may pass around the vibration source to be held by the mounting portion. Alternatively, the vibration source may simply sit on top of the mounting portion under the weight of gravity.

The first limb mounting portion L1H and the second limb mounting portion L2H each comprise a hook. The hook may extend in different directions. In <FIG>, the hooks extend perpendicularly to the first and second planes. In an alternative embodiment (see <FIG>) the hooks may extend parallel to the first and second planes. The hooks may be used to couple to openings or formations in the housing of the device in which the mounting is to be used. The hooks may be biased into those openings, respectively formations. For example, for the embodiment of <FIG>, the end sections L1SLAST (L1END) and L2SLAST (L2END) may be pulled together for insertion into the openings or formations. The hooks may function as assembly and alignment features.

At least one of the bends B1 to B4 and preferably each bend in the sequences of bends is a sharp bend and thus preferably has a bend radius less than or equal to <NUM> times the diameter of the wire.

The ends of the mounting portion MP are at opposite sides of a side-side symmetrical shape as shown. In the example of <FIG>, the first first limb section L1SFIRST and the last first limb section L1SLAST are near parallel, hence at an angle of between <NUM> and <NUM> degrees and the first second limb section L2SFIRST and the last second limb section L2SLAST are also near parallel, hence at an angle of between <NUM> and <NUM> degrees. The limbs thus form a U-shape in plan view. The first first limb section L1SFIRST and the first second limb section L2SFIRST may be parallel and side by side, as illustrated. The first first limb section L1SFIRST and the first second limb section L2SFIRST may lie in the first plane, as illustrated. The last first limb section L1SLAST and the last second limb section L2SLAST may be parallel or near parallel, hence at an angle of less than <NUM> degrees to each other. They may thus form a pair of supporting rails on opposite sides of the mounting portion MP.

As illustrated in <FIG>, the last first limb section L1SLAST and the last second limb section L2SLAST may each have a length greater than the maximum linear dimension of the mounting portion MP (i.e. the diameter of the loop). One end of each last limb section may be in front of the mounting portion and the other end may be behind the mounting portion. Thus, the last limb sections can provide a stable base for supporting the mounting portion on a support surface. They may provide support for vibrations which are perpendicular to the first and second planes or offset from that perpendicular direction.

By way of example, <FIG> show possible dimensions.

As shown, the mounting portion MP comprises a loop of diameter <NUM> (e.g. in the range <NUM> to <NUM>). The wire has a diameter <NUM> (e.g. in the range <NUM> to <NUM>). The first first limb section L1SFIRST and the first second limb section L2SFIRST are spaced by <NUM> (generally between <NUM>% and <NUM>% of the maximum dimension of the mounting portion).

The last first limb section L1SLAST and the last second limb section L2SLAST are at an angle of <NUM> degrees in this example and the maximum overall width is <NUM> (e.g. in the range <NUM> to <NUM>).

The offset between the two planes in this example is <NUM> (e.g. in the range <NUM>% to <NUM>% of the maximum dimension of the mounting portion, not referenced in the figures).

<FIG> show an embodiment with four bends per limb. <FIG> show an embodiment <NUM> in which the first and second sequences each comprise exactly two bends. <FIG> is a perspective view and <FIG> is a plan view. In this embodiment, the first first limb section L1SFIRST and the first second limb section L2SFIRST are collinear and extend outwardly (in opposite directions) from opposite sides of the mounting portion MP. The limbs in this design form an L-shape in plan view. Each limb thus has three sections; a first, second and last.

<FIG> shows the mounting <NUM> of <FIG> clipped to a base part <NUM> of a pump. The pump is one example of a possible vibration inducing component.

<FIG> shows the mounting <NUM> of <FIG> mounted on a pump support bracket <NUM> but supported loosely rather than being clipped to the base part of the pump. In <FIG>, the upward tilt of the mounting portion can be seen, because the mounting is not yet supporting the weight of the pump. When fully installed, the mounting portion is bent down to lie in a plane parallel with the support plane, i.e. parallel with the last limb sections.

As shown in <FIG>, the base part <NUM> of the pump may sit beneath the mounting <NUM>, and the mounting <NUM> is attached to the pump by clamping between the base part <NUM> of the pump and the main pump body.

<FIG> shows a complete pump assembly <NUM> in which the base part <NUM> has the mounting <NUM> of the type shown in <FIG>.

<FIG> shows a complete pump assembly <NUM> in which the mounting <NUM> of the type shown in <FIG> is clamped between the base part <NUM> of the pump and the main pump body.

Of course, any attachment approach for connecting to the pump may be used with any particular mounting embodiment.

<FIG> shows the pump assembly <NUM> of <FIG> mounted in a coffee machine, and <FIG> shows the pump assembly <NUM> of <FIG> mounted in a coffee machine. The internal parts of the coffee machine define a support surface <NUM> on which the last sections L1SLAST and L2SLAST rest. The mounting <NUM>, <NUM> is held to the support structure (of which the surface <NUM> is part) by the hooks L1H, L2H.

The support surface <NUM> provides support for downward movement of the mounting. All that is needed for the hooks L1H, L2H is that they are fitted in a way that resists upward movement. They may for example simply be inserted beneath a downward facing support surface or maneuvered into a retaining spigot as shown in <FIG>.

The coffee machine itself comprises a water reservoir, a coffee receptacle, a water heater and the pump for delivering water from the water reservoir to the water heater and/or to the coffee receptacle. The use of the mounting does not require any change to other features of the coffee machine, and hence a detailed discussion of known design features of coffee machines will not be presented.

For completeness, <FIG> show a coffee machine <NUM>. <FIG> shows a perspective view and <FIG> shows a view from in front. This example is a bean-to-cup machine, comprising a main body <NUM>, housing a water reservoir, a water heater and a reservoir for receiving coffee beans. There is an internal grinding mechanism for creating coffee grind, a brewing chamber or brew group for receiving the coffee grind, and a pumping system for pumping heated water through the coffee grind. The machine further comprises a drip tray <NUM>, an output tube <NUM> located over the drip tray <NUM> and a user interface <NUM> for receiving user selections. In other examples (not shown) the coffee machine <NUM> could be a capsule or pod machine, wherein the brewing chamber or brew group is designed to receive a (disposable) capsule or pod, filled with ground coffee.

The invention is not limited to coffee machines. It may be used in any domestic appliance with a pump or motor, such as an iron, steamer, vacuum cleaner, air cleaner, air humidifier, air dehumidifier, hair dryer, shaver, medical equipment etc..

The examples above show a mounting formed from a wire. The wire may have a circular cross section, but other profiles are possible, such as a solid square or rectangular cross section, or a hollow profile such a closed pipe or even an open hollow shape such as a U-shaped profile. The cross-sectional shape may also vary along the length of the wire. Changing the profile locally may be used to tune the bending rigidity in different directions and change the mass distribution along the wire, meaning that the effective operating window can be increased (with the aim of increasing fn_local). The wire may also be formed of multiple profiles which function together as one, such as stacked, wound, or interlocking components.

The examples above show three and five limb sections, but there may be many more, defining a more progressively curved shape. Increasing the number of limb sections distributes the load on each limb, allowing shorter limb wire lengths and thus a larger operating window (again with the aim of increasing fn_local). There is however the constraint that there are bends rather than a smooth curve, in particular discrete bends of <NUM> degrees or less.

Claim 1:
A system comprising:
a vibration inducing component;
a support surface; and
a vibration reducing mounting comprising a wire which follows a path which comprises:
a mounting portion (MP) supporting the vibration inducing component, the mounting portion comprising a path which is adapted to be in a first, horizontal, plane when in use with the weight of the component supported by the mounting portion, wherein the mounting portion (MP) comprises an open loop ring in the form of a loop which extends around at least <NUM> degrees and grips around a circumferential portion of the vibration inducing component and thereby retains it in position within the first plane, the ends of the open loop ring defining one end and an opposite end of the mounting portion;
a first limb (L1) extending outwardly from the one end of the mounting portion, wherein the first limb comprises a first sequence of bends (B) between a first first limb section (L1SFIRST) and a last first limb section (L1SLAST), and a first limb mounting portion (L1H) at the end of the last first limb section (L1SLAST); and
a second limb (L2) extending outwardly from the opposite end of the mounting portion (MP), wherein the second limb comprises a second sequence of bends (B) between a first second limb section (L2SFIRST) and a last second limb section (L2SLAST), and a second limb mounting portion (L2H) at the end of the last second limb section (L2SLAST),
wherein the last first limb section (L1SLAST) and the last second limb section (L2SLAST) lie in a second plane which is adapted, when in use, to be parallel with the first plane and which functions as a support plane, with the last first limb section (L1SLAST) and the last second limb section (L2SLAST) at opposing sides of the mounting portion (MP), and at least one of the bends of the first sequence and/or of the second sequence having an angle of <NUM> degrees or less,
and wherein the vibration inducing component is mounted to the mounting portion and the last first limb section and the last second limb section are mounted against the support surface.