FORM-2
THE PATENT ACT,1970
(39 OF 1970)
AND
THE PATENT RULES, 2003
(As Amended)
COMPLETE SPECIFICATION (See section 10;rule 13)
"SETTING TECHNOLOGY FOR RUBBER SURGING RESONANCE TO REDUCE HIGH-FREQUENCY DYNAMIC STIFFNESS OF
HYDRO MOUNTS"
We, Sujan Contitech AVS Pvt. Ltd., a corporation organized and existing under the laws of India, of F-11, Phase 3, MIDC Chakan, Taluka Khed, Pune –410 501, Maharashtra, India.

SETTING TECHNOLOGY FOR RUBBER SURGING RESONANCE TO REDUCE HIGH-FREQUENCY DYNAMIC STIFFNESS OF HYDRO MOUNTS
FIELD OF INVENTION
Embodiments of the present application illustrates on engine mounts, more specifically, hydraulic engine mounts that are designed to manage dynamic stiffness that is generated due to high frequency vibrations.
BACKGROUND OF THE INVENTION
Background description includes information that may be useful in understanding the present invention. It is not an admission that any of the information provided herein is prior art or relevant to the presently disclosed invention, or that any publication specifically or implicitly referenced is prior art.
In the current scenario, there are multiple designs of hydraulic vibration damping mounts that have been specially configured to work with powertrain purposes associated with automotive systems. The most common type of such hydraulic mounts is designed to experience a possibly unconstrained motion, which is in accordance with the vibrations that are generated, to generate a low dynamic stiffness of the hydraulic mount and eliminate vibrations that are in the lower amplitude range. Common designs of hydraulic mounts are generally developed with a range of frequency of resonance, for example, 150 Hz to 400 Hz, but however, the dynamic stiffness of the hydraulic mount occasionally rises significantly above and in range of frequencies beyond the designed frequency of resonance of the hydraulic mount. This is because the motion of the hydraulic mount is unable to counteract the variation in volume of the liquid that is present in the hydraulic mount. In view of this, the hydraulic mount is unable to isolate the vibrations that are beyond the resonant frequency range, and hence the engine experiences vibrations that are of higher frequency. These high frequency vibrations are mostly transferred on to the chassis and body of the automobile.
In prior art systems, several modifications have been introduced to counteract vibration related issues in hydraulic mounts and this is performed via, for example, constructing a form of cushioning using air column, where air is trapped between the decoupler of the hydraulic mount and an upper plate section. However, this kind of an arrangement cannot effectively reduce vibration because such an arrangement is unable to focus on certain specific

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frequencies, but only provide an overall cushioning effect over a range of frequencies of vibration. Therefore, taking into consideration of all these aspects, there is a need for a device to reduce dynamic stiffness in hydraulic mounts.
SUMMARY OF THE INVENTION
The following presents a simplified summary of the subject matter to provide a basic understanding of some of the aspects of subject matter embodiments. This summary is not an extensive overview of the subject matter. It is not intended to identify key/critical elements of the embodiments or to delineate the scope of the subject matter. Its sole purpose to present some concepts of the subject matter in a simplified form as a prelude to the more detailed description that is presented later.
Disclosed herein is a hydraulic mount for establishing rubber surging resonance with the aim to reduce high-frequency dynamic stiffness of hydraulic mounts. Referring to FIGURES 1A-1C, the hydraulic mount (10) is designed to reduce dynamic stiffness peak and comprises an upper stopper element (2), a lower outer tube (3), and multiple rubber feet (tA, tB, tC, and tD). The upper stopper element (2) comprises an inner tube (4) and the lower outer tube (3) is positioned below the upper stopper element (2). The rubber feet (tA, tB, tC, and tD) are positioned in zones (1a, 1b, 1c, 1d), which is between the inner tube (4) and the lower outer tube (3). At least two rubber feet members ([tA and tB] or [tC and tD]) that are positioned between the inner tube (4) and the lower outer tube (3) in the hydraulic mount (10) reduces the dynamic stiffness peak by coupling the surging resonance of the at least two rubber feet ([tA and tB] or [tC and tD]).
In an embodiment, at least two rubber feet members (tA and tB) are positioned between the inner tube (4) and the lower outer tube (3) in the hydraulic mount (10) reduces the dynamic stiffness peak by coupling the surging resonance of the two rubber feet (tA and tB). In an embodiment, at least two rubber feet members (tC and tD) are positioned between the upper stopper element (2) and the lower outer tube (3) reduces the dynamic stiffness peak by coupling the surging resonance of the two rubber feet (tC and tD), wherein the rubber feet (tA, tB, tC, and tD) that are positioned in zone (1a), zone (1b), zone (1c), and zone (1d) form a coupling surging resonance, which reduces the dynamic stiffness caused due to resonance.

In an embodiment, at least two pairs of the rubber feet ([tA and tB] or [tC and tD]) are positioned between the upper stopper element (2) and the lower outer tube (3), which couples surging resonance in at least X direction and Y direction, wherein the coupling of two sets of surging resonance across the X direction and the Y direction causes the dynamic stiffness peak to be reduced in a wide frequency band range of 500 Hz to 2000 Hz. In an embodiment, each rubber foot (tA, tB, tC, and tD) is designed with a variable thickness depending on the design of the hydraulic mount (10), wherein thickness of rubber feet (tA, tB, tC, and tD) are different from each other to compensate for a wide range of frequency changes and corresponding vibrations. In an embodiment, hydraulic mount (10) further comprises positioning of at least 3 or more pairs of rubber feet (tA, tB, tC, and tD) across multiple zones to couple the surging resonance across three or more sets of surging resonance, wherein the peak dynamic stiffness peak is further reduced in a wide frequency band range of 500 to 2000Hz.
In an embodiment, the hydraulic mount (10) is floated using rubber, wherein the surging resonance of each rubber feet (tA, tB, tC, and tD) causes the hydraulic mount (10) to operate with an increase in the volume of a main liquid chamber, which creates a mode in which the dynamic rigidity decreases. In an embodiment, hydraulic mount (10) is constructed with three or more pairs of rubber feet (tA, tB, tC, or tD) that couple the surging resonance, wherein higher frequency resonance of the rubber feet (tA, tB, tC, or tD) is varied by varying mass and static stiffness of the rubber in zones (1a, 1b, 1c, and 1d), wherein the variation in thickness of the rubber feet (tA, tB, tC, and tD) inherently varies the mass and static stiffness of each rubber foot (tA, tB, tC, or tD) in each zone (1a, 1b, 1c, and 1d), which generates a variable surging resonance to compensate for variation in frequency of vibrations.
In another embodiment, the hydraulic mount (10) is constructed with one or more pairs of rubber feet (tA, tB, tC, or tD) that couple the surging resonance, wherein higher frequency resonance of the rubber feet (tA, tB, tC, or tD) is varied by varying mass and static stiffness of the rubber in zones (1a, 1b, 1c, and 1d), wherein the variation in thickness of the rubber feet (tA, tB, tC, and tD) inherently varies the mass and static stiffness of each rubber foot (tA, tB, tC, or tD) in each zone (1a, 1b, 1c, and 1d), which generates a variable surging resonance to compensate for variation in frequency of vibrations. with device unit (8) floated in rubber, wherein the surging resonance of each rubber feet (tA, tB, tC, and tD) causes the hydraulic

mount (10) to operate with an increase in the volume of a main liquid chamber (7) which creates a mode in which the dynamic rigidity decreases.
BRIEF DESCRIPTION OF THE ACCOMPANYING DRAWINGS
The following drawings are illustrative of particular examples for enabling systems and methods of the present disclosure, are descriptive of some of the methods and mechanism, and are not intended to limit the scope of the invention. The drawings are not to scale (unless so stated) and are intended for use in conjunction with the explanations in the following detailed description.
FIGURES 1A exemplarily illustrates a top perspective view of the hydraulic mount, as an example embodiment of the present disclosure.
FIGURE 1B exemplarily illustrates a sectional internal view of the hydraulic mount along X-X axis, as an example embodiment of the present disclosure.
FIGURE 1C exemplarily illustrates a sectional internal view of the hydraulic mount along Y-Y axis, as an example embodiment of the present disclosure.
FIGURE 2 exemplarily illustrates a graph that predicts dynamic stiffness model based on the improved hydraulic mount, as an example embodiment of the present disclosure.
Persons skilled in the art will appreciate that elements in the figures are illustrated for simplicity and clarity and may represent both hardware and software components of the system. Further, the dimensions of some of the elements in the figure may be exaggerated relative to other elements to help to improve understanding of various exemplary embodiments of the present disclosure. Throughout the drawings, it should be noted that like reference numbers are used to depict the same or similar elements, features, and structures.
DETAILED DESCRIPTION OF THE INVENTION
Exemplary embodiments now will be described. The disclosure may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided so that this disclosure will be thorough and

complete, and will fully convey its scope to those skilled in the art. The terminology used in the detailed description of the particular exemplary embodiments illustrated in the accompanying drawings is not intended to be limiting. In the drawings, like numbers refer to like elements.
It is to be noted, however, that the reference numerals used herein illustrate only typical embodiments of the present subject matter, and are therefore, not to be considered for limiting of its scope, for the subject matter may admit to other equally effective embodiments.
The specification may refer to “an”, “one” or “some” embodiment(s) in several locations. This does not necessarily imply that each such reference is to the same embodiment(s), or that the feature only applies to a single embodiment. Single features of different embodiments may also be combined to provide other embodiments.
As used herein, the singular forms “a”, “an” and “the” are intended to include the plural forms as well, unless expressly stated otherwise. It will be further understood that the terms “includes”, “comprises”, “including” and/or “comprising” when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof. It will be understood that when an element is referred to as being “connected” or “coupled” to another element, it can be directly connected or coupled to the other element or intervening elements may be present. Furthermore, “connected” or “coupled” as used herein may include operatively connected or coupled. As used herein, the term “and/or” includes any and all combinations and arrangements of one or more of the associated listed items.
Unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure pertains. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.

Referring to FIGURES 1A-1C, FIGURE 1A exemplarily illustrates a top perspective view of the hydraulic mount (10), as an example embodiment of the present disclosure. The hydraulic mount (10) comprises a stopper member (2) or an upper stopper element (2) comprising an inner tube (4), that’s upwardly positioned and an outer tube or lower outer tube (3). The main rubber element (1), herein after referred to as “rubber feet” is positioned in zones marked (1a, 1b, 1c, 1d), which is between the stopper member (2) and the lower outer tube (3). FIGURE 1B exemplarily illustrates a sectional internal view of the hydraulic mount (10) along X-X axis, as an example embodiment of the present disclosure. Precisely, the main rubber element (1) or the rubber foot is positioned between the lower outer tube (3) and the inner tube (4), as shown in FIGURE 1B. Furthermore, a decoupler (6) is positioned within the device unit (8), which is below the rubber feet (1) and the outer metal portion (3). The decoupler (6) provides a low restriction to fluid flow, it becomes the preferred flow path, and acts on reducing the damping coefficient of the hydraulic mount (10) in low excitation like idle frequency as results our decoupler low dynamic stiffness in low amplitude excitation. FIGURE 1C exemplarily illustrates a sectional internal view of the hydraulic mount (10) along Y-Y axis, as an example embodiment of the present disclosure.
As shown in FIGURES 1B and 1C, the rubber feet (tA, tB, tC, and tD) are positioned in zones (1a, 1b, 1c, 1d), which is between the inner tube (4) and the lower outer tube (3). Or in other words, two rubber feet members (tA and tB) are introduced (FIGURE 1B) between the upper stopper element (2) (comprising the inner tube (4)) and the lower outer tube (3) (or outer metal portion) in the hydraulic mount (10) to reduce the dynamic stiffness peak by coupling the surging resonance of the two rubber feet (tA and tB). Similarly, two rubber feet members (tC and tD) are introduced (FIGURE 1C) between the inner tube (4) and the lower outer tube (3) in the hydraulic mount (10) to reduce the dynamic stiffness peak by coupling the surging resonance of the two rubber feet (tC and tD). In effect, the peak of dynamic stiffness because of the resonance is reduced by coupling surging resonance of each rubber foot (tA, tB, tC, and tD). In other words, the rubber feet (tA, tB, tC, and tD) that are positioned in zone (1a), zone (1b), zone (1c), and zone (1d) form a coupling surging resonance, which reduces the dynamic stiffness caused due to resonance.
At least two pairs of rubber feet ([tA and tB] or [tC and tD]) are positioned between the inner tube (4)) and the lower outer tube (3), which couple surging resonance in both directions, for example, X direction and Y direction. The coupling of two sets of surging resonance causes

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the dynamic stiffness peak to be reduced in a wide frequency band, for example, 500 to 2000Hz. Therefore, the two instances comprise (1) reducing the dynamic stiffness peak by coupling surging resonance of the two rubber foot parts (tA and tB) of section X-X and (2) reducing the dynamic stiffness peak by coupling the surging resonance of the two rubber feet (tC and tD) of section Y-Y. It is to be noted that each rubber foot (tA, tB, tC, and tD) is designed with a variable thickness depending on the design of the engine mount. It means that thickness of rubber foot (tA, tB, tC, and tD) are different from each other to compensate for a wide range of frequency changes and corresponding vibrations. In another embodiment, at least 3 or more pairs of rubber feet (tA, tB, tC, and tD) are introduced across multiple zones (1a, 1b, 1c, 1d) to couple the surging resonance. By coupling three or more sets of surging resonance, the peak dynamic stiffness peak can be further reduced in a wide frequency band (500-2000Hz). The hydraulic mount (10) is designed with multiple zones (1a, 1b, 1c, 1d), and each rubber foot (tA, tB, tC, tD) is added to each zone (1a, 1b, 1c, 1d) so that the peak dynamic stiffness is further reduced to a desired range.
The hydraulic mount (10) unit with device unit (8) floated in rubber, or in other words, the unit device (8) or orifice is supported top and bottom of edge with rubber. The surging resonance of the rubber feet causes the hydraulic mount (10) unit to operate with an increase in the volume of a main liquid chamber (7), which creates a mode in which the dynamic rigidity decreases. While the rubber feet (tA, tB, tC, and tD) resonates, the main liquid chamber (7) will become bigger or will increase in volume, which creates a new mode that allows the hydraulic mount (10) to float, eventually reducing the dynamic stiffness. For example, the hydraulic mount (10) is designed with three or more pairs of rubber feet (tA, tB, tC, and tD) that couple the surging resonance. The higher frequency resonance of the rubber feet (tA, tB, tC, and tD) is varied by varying mass and static stiffness of the rubber in zones (1a, 1b, 1c, 1d). In other words, each rubber foot (tA, tB, tC, and tD) is designed with a variable thickness depending on the design of the hydraulic mount (10). The variation in thickness of the rubber foot (tA, tB, tC, or tD) inherently varies the mass and static stiffness of each rubber foot (tA, tB, tC, and tD) in each zone (1a, 1b, 1c, or 1d). Such variation in thickness generates a variable surging resonance to compensate for variation in frequency of vibrations. A combination of: at least two pairs of rubber feet, for example, [tA and tB] or [tC and tD], for coupling surging resonance in both directions (X direction and Y direction) and varying the frequency resonance of the rubber feet (tA, tB, tC, and tD) by varying mass and static stiffness of the rubber in zones (1a, 1b, 1c, 1d), reduces the dynamic stiffness peak in

the range of 500Hz to 2000Hz band. Furthermore, a combination of three or more pairs of rubber feet (tA, tB, tC, and tD) that couple surging resonance and varying mass and static stiffness of the rubber in zones (1a, 1b, 1c, 1d), further reduces the dynamic stiffness peak in the 500 Hz to 2000 Hz band.
In another embodiment, the hydraulic mount (10) is constructed with one or more pairs of rubber feet (tA, tB, tC, or tD) that couple the surging resonance, wherein higher frequency resonance of the rubber feet (tA, tB, tC, or tD) is varied by varying mass and static stiffness of the rubber in zones (1a, 1b, 1c, and 1d), wherein the variation in thickness of the rubber feet (tA, tB, tC, and tD) inherently varies the mass and static stiffness of each rubber foot (tA, tB, tC, or tD) in each zone (1a, 1b, 1c, and 1d), which generates a variable surging resonance to compensate for variation in frequency of vibrations. with device unit (8) floated in rubber, wherein the surging resonance of each rubber feet (tA, tB, tC, and tD) causes the hydraulic mount (10) to operate with an increase in the volume of a main liquid chamber (7) which creates a mode in which the dynamic rigidity decreases.
FIGURE 2 exemplarily illustrates a graph that predicts dynamic stiffness model based on the improved hydraulic mount (10) (as shown by dotted lines in FIGURE 2), as an example embodiment of the present disclosure. As shown in FIGURE 2, the conventional hydraulic mount (10) is shown using the solid line. The graph shows the variation of dynamic stiffness across varying frequencies from 0 to 1000Hz and above. As shown in the graph, the dynamic stiffness (N/mm) is the same for conventional hydraulic mounts (10) and the hydraulic mount (10) that is explained in the present disclosure. However, just before 200 Hz of frequency, the conventional hydraulic mounts (10) show a considerable rise in the dynamic stiffness, whereas the hydraulic mount (10) of the present disclosure displays a relatively reduced variation in dynamic stiffness. Based on the hydraulic mount (10) of the present disclosure, the peaks and lows of dynamic stiffness variation in the graph are respectively indicated in the zones, for example, zone (1a), zone (1b), zone (1c), and zone (1d), where rubber feet of variable thickness (tA, tB, tC, and tD), which are positioned to form a coupling surging resonance, which reduces the dynamic stiffness caused due to resonance. Hence, this graph provides a predictive analysis for the type of thickness of the rubber feet to be used during construction of the hydraulic mount (10).

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Current invention has been discussed specifically with full disclosure. However, numerous changes can be made in the detail of structures, combinations, and part arrangement along with technical advancements that will be implemented in near future without changing the spirit and scope of the invention.
Although the invention has been described with reference to specific embodiments, this description is not meant to be construed in a limiting sense. Various modifications of the disclosed embodiments, as well as alternate embodiments of the invention, will become apparent to persons skilled in the art upon reference to the description of the invention. It is therefore, contemplated that such modifications can be made without departing from the scope of the present invention as defined.

We claim:
1. A hydraulic mount (10) to reduce dynamic stiffness peak comprising:
an upper stopper element (2) comprising an inner tube (4);
a lower outer tube (3) positioned below the upper stopper element (2);
a plurality of rubber feet (tA, tB, tC, and tD) that are positioned in zones (1a, 1b, 1c, 1d), which is between the inner tube (4) and the lower outer tube (3),
wherein at least two rubber feet members ([tA and tB] or [tC and tD]) that are positioned between the inner tube (4) and the lower outer tube (3) in the hydraulic mount (10) reduces the dynamic stiffness peak by coupling the surging resonance of the two rubber feet ([tA and tB] or [tC and tD]).
2. The hydraulic mount (10) as claimed in claim 1, wherein at least two rubber feet members (tA and tB) are positioned between the inner tube (4) and the lower outer tube (3) in the hydraulic mount (10) reduces the dynamic stiffness peak by coupling the surging resonance of the two rubber feet (tA and tB).
3. The hydraulic mount (10) as claimed in claim 2, wherein at least two rubber feet members (tC and tD) that are positioned between the upper stopper element (2) and the lower outer tube (3) reduces the dynamic stiffness peak by coupling the surging resonance of the two rubber feet (tC and tD), wherein the rubber feet (tA, tB, tC, and tD) that are positioned in zone (1a), zone (1b), zone (1c), and zone (1d) form a coupling surging resonance, which reduces the dynamic stiffness caused due to resonance.
4. The hydraulic mount (10) as claimed in claim 1, wherein at least two pairs of the rubber feet ([tA and tB] or [tC and tD]) are positioned between the inner tube (4) and the lower outer tube (3), which couples surging resonance in at least X direction and Y direction, wherein the coupling of two sets of surging resonance across the X direction and the Y direction causes the dynamic stiffness peak to be reduced in a wide frequency band range of 500 Hz to 2000 Hz.
5. The hydraulic mount (10) as claimed in claim 1, wherein each rubber foot (tA, tB, tC, and tD) is constructed with a variable thickness depending on the design of the hydraulic

mount (10), wherein thickness of rubber feet (tA, tB, tC, and tD) are different from each other to compensate for a wide range of frequency changes and corresponding vibrations.
6. The hydraulic mount (10) as claimed in claim 1, further comprising positioning of at least 3 or more pairs of rubber feet (tA, tB, tC, and tD) across multiple zones to couple the surging resonance across three or more sets of surging resonance, wherein the peak dynamic stiffness peak is further reduced in a wide frequency band range of 500 to 2000Hz.
7. The hydraulic mount (10) as claimed in claim 1 is with device unit (8) floated in rubber, wherein the surging resonance of each rubber feet (tA, tB, tC, and tD) causes the hydraulic mount (10) to operate with an increase in the volume of a main liquid chamber (7) which creates a mode in which the dynamic rigidity decreases.
8. The hydraulic mount (10) as claimed in claim 5 is constructed with three or more pairs of rubber feet (tA, tB, tC, or tD) that couple the surging resonance, wherein higher frequency resonance of the rubber feet (tA, tB, tC, or tD) is varied by varying mass and static stiffness of the rubber in zones (1a, 1b, 1c, and 1d), wherein the variation in thickness of the rubber feet (tA, tB, tC, and tD) inherently varies the mass and static stiffness of each rubber foot (tA, tB, tC, or tD) in each zone (1a, 1b, 1c, and 1d), which generates a variable surging resonance to compensate for variation in frequency of vibrations.
9. The hydraulic mount (10) as claimed in claim 7 is constructed with one or more pairs of rubber feet (tA, tB, tC, or tD) that couple the surging resonance, wherein higher frequency resonance of the rubber feet (tA, tB, tC, or tD) is varied by varying mass and static stiffness of the rubber in zones (1a, 1b, 1c, and 1d), wherein the variation in thickness of the rubber feet (tA, tB, tC, and tD) inherently varies the mass and static stiffness of each rubber foot (tA, tB, tC, or tD) in each zone (1a, 1b, 1c, and 1d), which generates a variable surging resonance to compensate for variation in frequency of vibrations. with device unit (8) floated in rubber, wherein the surging resonance of each rubber feet (tA, tB, tC, and tD) causes the hydraulic mount (10) to operate with an increase in the volume of a main liquid chamber (7) which creates a mode in which the dynamic rigidity decreases. fj\ ^jj^