In tyre sound absorber

This invention relates to an in-tyre sound absorber for the reduction of tonal sounds in pneumatic tyres.

Tonal sound is caused by a standing wave generated in the space between the tyre and wheel rim. This standing wave relates to the geometry of the tyre, and the temperature and pressure of the air in the tyre cavity. The resultant tone or sound is typically below 600 Hz.

The problem of tonal noise transmission into the motor vehicle cabins has been addressed by a number of means. US Patent 6,755,483 (Sumitomo Rubber Industries, Ltd.) describes the use of a noise damper disposed in the cavity formed between the rim and the tyre. The noise damper is made from porous material which has a specific density of between 0.005 and 0.06 and in particular an open-cell polyurethane foam. In one embodiment, the noise damper has an uneven facing, or is made from an outer layer having low sound reflection and an inner layer, adjacent the wheel rim, having high sound absorption.

However, it is often a problem with the prior art that the noise damper can be damaged during fitment of the tyre on the wheel rim or the noise damper is not physically strong enough to resist tearing or breaking apart during normal operation.

It is an object of the invention to overcome, or at least ameliorate, some of the above problems or at least provide an alternative in-tyre silencer material and a system utilising the in-tyre silencer material.

Accordingly in one aspect, the present invention is an in-tyre sound absorber for a pneumatic wheel assembly including a wheel rim and a tyre fitted to the wheel rim, the sound absorber comprising a first fibrous layer and a second fibrous layer, the second layer having a higher air flow resistance than the first layer, and being configured to fit around the wheel rim with the first layer in contact with a surface of the wheel rim and extending substantially between the second layer and the wheel rim.

The low air flow resistance of the first layer allows the standing sound pressure wave to propagate within the layer where the particle velocity of the radial pressure wave that creates the tonal noise is in a normal direction to the direction of the pressure wave. The excited air particles are thereby forced through the high air flow resistance of the second layer to provide the sound absorption.

Preferably the first and second layers are made from non- woven fibrous webs. In a preferred embodiment, the first fibrous layer has fibres orientated substantially perpendicular to the surface of the wheel rim. The orientation substantially perpendicular to the surface of the wheel rim provides an increased tensile strength of the sound absorber in the direction perpendicular to the surface of the wheel rim when contrasted with conventional bulky non-woven fabrics in which the fibres are cross-lapped. This is particularly advantageous for the present invention where the centrifugal forces increase with the rotational speed of the wheel during operation and the increased tensile strength in the direction perpendicular to the surface of the wheel rim decreases the risk of delamination of the sound absorber.

Preferably, the air flow resistance of the respective layers is substantially consistent to provide a relatively constant acoustic absorption to reduce the tonal noise. More preferably the ratio of air flow resistance of the second layer to the first layer is between 25:1 and 35:1. That is the air flow resistance of the second layer is between 25 and 35 times that of the first layer. Even more preferably the ratio is approximately 30: 1.

Preferably the spatial average of the air flow resistance of the second layer is between 400 and 1000 Rayls. More preferably in the range of 600-800 Rayls.

Preferably the spatial average of the flow resistivity of the spacer layer is in the range of 800-8000 Rayls/m. Most preferably 2000-4000 Rayls/m.

Preferably the first layer of the sound absorber is made from a fibrous web of polyester fibres. More preferably, the second layer of the sound aborber is made from a fibrous web of polyester fibres.

According to another aspect the present invention is a tyre sound absorbing system including a tyre, a wheel rim, the wheel rim and tyre forming an enclosed tyre cavity, and a porous insert disposed adjacent a surface of the wheel rim within the tyre cavity, the porous insert comprising an inner fibrous layer proximal to the wheel rim surface and an outer fibrous layer distal to the wheel rim surface, the outer fibrous layer has a higher air flow resistance than the inner fibrous layer, and wherein the porous insert is shaped to avoid damage during fitment of the tyre on the rim.

The porous insert is shaped so that the bead of the tyre is able to push aside the sound absorber during fitment so that damage to the sound absorber is avoided. Preferably the porous insert has rounded edges to assist the tyre bead in pushing the sound absorber to a position where the risk of damage is reduced. Even more preferably the rounded edges are formed by thermoforming. The rounded edges can be slit or notched to avoid creasing of the porous insert.

Preferably the porous fibrous insert is removably attached to the wheel rim. Even more preferably a hook and loop attachment means is used wherein the loops are formed by the inner fibrous layer and the hooks are attached to the wheel rim.

Brief Description of the Drawings

Preferred embodiments of the present invention will now be described by way of example only with reference to the below figures.

Figure 1 is a cross-sectional view of an in-tyre sound absorber according to one embodiment of the invention.

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Figure 2 is a cross-sectional view of the in-tyre sound absorbing system using the in-tyre sound absorber of Figure 1 installed on a wheel rim.

Figure 3 is a cross-sectional view of an in-tyre sound absorbing system using the in-tyre sound absorber of Figure 1 according to another embodiment. Figure 4A is a bottom plan view of a tongue and slot joining system for the in-tyre sound absorber of Figure 1.

Figure 4B is a cross-sectional view of a tongue and slot joining system for the in-tyre sound absorber of Figure 1.

Figure 5 is a cross-sectional view of an in-tyre sound absorber according to an alternative embodiment of the invention

Figure 6A to 6C are graphs of the Noise versus Frequency of the test results of Example 1.

Detailed Description

Referring to Figures 1-4 the in-tyre sound absorber 1 is comprised of a first layer 3 of a thermoformable acoustic sheet, backed with a second layer 5 of a spacing layer of vertically lapped 3 -dimensional thermally bonded non- woven fabric. The thermoformable acoustic sheet 3 is laminated to the vertically lapped fabric 5 using a thermoplastic adhesive 7 that is permeable. The sound absorber 1 is installed on a wheel rim 9 to absorb at least some of the tonal noise of the tyre.

The thermoformable acoustic sheet 3 is prepared generally in accordance with the applicant's International patent application published as WO 02/09089. The thermoformable acoustic sheet 3 is formed using polyester fibre, has an air flow resistance between 400 and 1000 Rayls and a high resistance to tearing. Alternatively, the sheet 3 can be formed from polypropylene or other suitable fibre. The sheet 3 has a thickness of approximately 0.5-lmm, and a mass of approximately 50-250g/m ² .

The vertically lapped fabric 5 is also made of polyester fibres. An advantage of the two layers 3, 5 being made of the same material is that the sound absorber 1 is recyclable.

When installed the fibres in the fabric 5 are generally orientated in the radial direction

because of the vertically lapped structure of the fabric 5. This provides additional strength to prevent separation of the sound absorber 1 due to the centrifugal forces encountered during normal operation of the wheel. The flow resistivity of the spacer layer 5 is less than that of the thermoformable acoustic sheet 3 and is between 800 and 8000 Rayls/m.

Prior to installation on the wheel rim 9, the edges 11 of the thermoformable acoustic sheet 3 are moulded to provide a rounded edge to the sound absorber 1 so that the risk of tearing of the sound absorber 1 during fitment of the tyre on the wheel rim 9 is reduced. This occurs because the tyre bead is able to push aside the sound absorber 1 during fitment and there are no sharp edges to catch on. Thus it is possible to install a tyre on the wheel rim 9 without damaging the sound absorber 1 and without using a special groove in the wheel rim 9 to shelter the absorber 1. The radius on the sound absorber edge 11 is typically in the range of 15 -20mm.

An added advantage of the rounded edges 11 and high tear resistance of the thermoformable acoustic sheet 3 is that the sound absorber 1 also resists damage from a tyre lever during removal of the tyre. This makes the sound absorber 1 suitable for use on the wheel rim 9 with a number of tyres, prolonging the life of the sound absorber 1.

To provide the necessary sound absorption, the low air flow resistance of the spacing layer 5 allows the standing sound pressure wave to propagate within the spacing layer 5. The particle velocity of the radial pressure wave that creates the tonal noise is in a normal direction to the direction of the pressure wave. Thus the excited air particles are forced through the high air flow resistance thermoformable acoustic sheet 3 which provides the sound absorption.

The sound absorber 1 is attached to the wheel rim 9 by an adhesive, mechanical fastening, or a combination of both. The adhesive, mechanical fastening or combination must securely hold the sound absorber 1 in place during replacement of the tyre whilst still allowing the tyre bead to push the sound absorber 1 aside during installation.

In the embodiment shown in Figure 3, a hook and loop attachment means is used to attach the sound absorber 1 to the wheel rim 9. The vertically lapped spacer material 5 provides the loops and the hooks 13 are attached to the wheel rim 9. In this arrangement the sound absorber 1 is able to be replaced with another sound absorber if the sound absorber 1 becomes ineffective or the tyre on the wheel rim changes sufficiently that a sound absorber with slightly different properties would be more suited to the new configuration of the wheel rim 9 and tyre.

In order to assist the attachment of the sound absorber 1 to the wheel rim 9, the two ends of the sound absorber 1 can be connected together by means of a fastening arrangement after the sound absorber has been attached to the wheel rim 9. The fastening arrangement 14 shown in Figures 4a and 4b uses a tongue 15 and slot 17 arrangement in the ends of the thermoformable acoustic sheet 3 to effectively form a torus around the wheel rim. An adhesive is also used to secure the sound absorber 1 onto the wheel rim.

In an alternative embodiment, the two ends of the sound absorber may be connected by a hook and loop fastening arrangement, wherein the hook section is affixed to one end of the sound absorber by sewing, gluing or thermal staking, and the loop section is affixed to the other end by similar means.

Other methods of connecting the two ends of the sound absorber 1 may be employed, without departing from the purpose of the invention, such as stapling, rivetting, glueing.

In practical embodiments, the thickness of the sound absorber 1 is between 12 to 40mm and more typically between 20 to 30mm thick, althought he thickness used in an actual installation will depend on physical and acoustical requirements. The maximum practical height of the spacer layer 5 is normally about 25mm.

The sound absorber 1 is normally between 50 to 150mm wide depending upon the shape and configuration of the wheel rim 9. However in most wheel rims, the width is between

50 to 100mm. The width of the sound absorber 1 is generally kept to a minimum without

affecting the sound absorption as the wider the sound absorber, the more it affects fitting and removal of the tyre. The preferred width is in the range of 70-100mm. At more than 100mm wide, the likelihood of the tyre bead catching the sound absorber 1 and may prevent the tyre from sealing properly.

The sound absorber can be made to a length that is substantially equal to the circumference of the wheel rim, so that each wheel size requires a different length. Alternatively, the length of the sound absorber could be created by cutting excess material from a sound absorber of a standard length. In this embodiment, a fabric may be laminated on the second layer to provide the loops for a hook and loop fastening arrangement where a hook section was attached to one end of the sound absorber. In this arrangement, the hook and loop fastening arrangement could be used regardless of the amount removed from the standard sound absorber length.

In an alternative embodiment shown in Figure 5, the edges 21 of the sound absorber 23 are moulded such that the second layer 25, a thermoformable acoustic sheet, extends along a substantial portion of the sides of the sound absorber 21. The extension of the thermoformable acoustic sheet 25 along the sides of the sound absorber 21 increases the resistance of the sound absorber 21 to damage to the first layer 27, a vertically lapped fabric, during tyre fitment.

As the curvature of sound absorber decreases with the thickness of the sound absorber when installed on the wheel rim, the edges of the thermoformable acoustic sheet 3 may be slit at regular intervals along the length of the sound absorber. This provides for overlapping of the edge at these intervals of the thermoformable to reduce the liklihood of humps forming in the sound absorber and thereby making tyre fitment more difficult. Alternatively, the edges of the thermoformable acoustic sheet are notched. It should also be noted that the sound absorber may be moulded on a circular moulding tool so that the curvature of the sound absorber is substantially permantently moulded into the sound absorber.

Example 1

A prototype tyre sound absorber, according to this invention with a lower air flow resistance spacer layer and a higher air flow resistance thermoformable acoustic sheet, were made up and attached to alloy wheel rims using a pressure sensitive adhesive. Low profile tyres were then fitted to the rim in the normal manner.

The alloy wheel rims were 18 inches diameter by 8 inches wide and the tyres were Pontenza RE55S, 265/35ZR18.

The sound absorber measured 20mm thick, 90mm wide and moulded with a radius on the leading edge.

The sound absorber had a thermoformable acoustic sheet with a measured spatial average flow resistance of 600 Rayls, and weighed 180g/m ² , with a thickness of approximately 0.5mm.

The spacer layer had a density of 600g/m ² , and consisted of a blend of polyester fibres with an average fibre size of 6-denier. The spacer consisted of 30% polyester bicomponent fibre and 70% polyester staple fibre. The spatial average air flow resistance of the spacer layer was about 20 Rayls or approximately 1/3 Oth the spatial average air flow resistance of the thermorformable acoustic sheet.

The wheel, fitted with the tyre and the sound absorber, as described above, was suspended freely from a chain and allowed to gently touch an electromagnetic shaker, which was used to excite the whole assembly. An accelerometer was connected to the shaker to measure the input excitation signal. Another accelerometer was attached to the tyre, and the transfer function was measured using 2-channel a signal analyser.

Tests were conducted at two excitation spots on the tyre and data obtained at 16 different measuring points for each excitation spot, and the results similarly recorded. The results of three measuring points, which are representative of the transfer functions of all of the tests conducted, are shown in Figures 6A, 6B and 6C. The area under the curves was integrated to determine the total power content and was compared to a total power content measured of the tyre without the in-tyre silencer installed. By subtracting the power content in these examples, the anticipated reduction in power content, in the frequency range from zero to 600Hz, was then calculated.

There was a consistent reduction in the acoustic energy propagated inside the tyre. The total reduction in power content was within the range of 5.5 to 9 decibels, depending on the position of the measurement.

Such a reduction will be translated into a reduction of vibrational excitation between the tyre, the vehicle suspension, and the vehicle body, resulting in an audible noise reduction within the vehicle. The actual noise reduction within the vehicle is dependant on the sensitivity of the transmission path between the tyre and the vehicle interior.

The foregoing describes only certain embodiments of the invention and modifications can be made without departing from the scope of the invention.