Lateral vibration isolator mechanism for vehicle seat backs

Abstract

To provide a vehicle seat.SOLUTION: A vehicle seat includes a first seat component such as a seat pan or seat frame, and a second seat component such as a seat back. The first seat component is rotatably coupled to the second seat component by a rotatable coupling, and a laterally oriented vibration isolator is positioned between the first seat component and the second seat component at the rotatable coupling. Transmission of vibration from the first seat component to the second seat component through the rotatable coupling is suppressed by the vibration isolator. In some cases, the vibration isolator is a quasi-zero-stiffness (QZS) isolator.SELECTED DRAWING: Figure 7

Description

[Technical Field]

[0001] The subject matter described in this invention relates to a lateral vibration isolator mechanism for a vehicle seat back that is particularly, but not exclusively, useful for reducing seat vibration in cars, trucks, and wagons. [Background technology]

[0002] Seats in vehicles (e.g., cars, trucks, or vans) often include a seat pan or seat cushion pan attached to a seat frame, which is itself attached to a pair of slide rails that are attached to the vehicle floor. To limit the transmission of vibrations between the vehicle floor and the seat, a vibration isolator can be installed between the slide rails and the seat frame or between the slide rails and the floor. For example, a linear spring vibration isolator can be used for this purpose. However, vibrations can still be felt within the seat base (e.g., the seat pan and / or seat frame) and can be transmitted from the seat base to the seat back. Because the seat back is taller than the other seat components, any lateral (e.g., side-to-side) vibrations within the seat base result in greater movement at the top of the seat back than at the bottom. Therefore, it can be said that the seat back amplifies vibrations, such that, for example, an occupant's head will feel more vibration than a lower portion of the same occupant's back. Therefore, a need exists for a vibration isolation mechanism to limit vibrations in the seat back.

[0003] The information contained in this Background section of the specification, including any references cited herein and any explanation or discussion therein, is included for technical reference purposes only and should not be considered as subject matter that should bind the scope of the disclosure. Summary of the Invention

[0004] To reduce the transmission of vibration along any given axis, stacked disk isolators or quasi-zero stiffness (QZS) isolators can be utilized. By appropriate selection of spring design parameters, a spring stack can be designed to produce a quasi-zero / negative stiffness response for a range of forces applied to the spring stack. A quasi-zero stiffness response occurs when the spring stack compresses or decompresses very easily in response to changes in the applied force, as if it had a stiffness or spring constant close to zero. For example, when subjected to a force within this design range (e.g., when compressed into its quasi-zero stiffness range), the spring stack can deflect over a relatively wide range of values ​​in response to small or no increases in the applied force. Alternatively, when the spring stack is in its quasi-zero stiffness range, it may not "push back" against compressive forces, but rather may simply absorb these changes by compressing or "deflecting." Under these conditions, the spring stack can move from a first element (e.g., a vehicle seat bottom) to a second element (e.g., a vehicle seat bottom). Sheet It has been discovered that the transmission of vibrations to the back can be eliminated or substantially attenuated.

[0005] In some cases, it may be desirable to apply sufficient axial preload force on the spring stack to bring the stack into a near-zero / negative stiffness response range so that maximum benefit of the isolation device can be realized. Furthermore, the spring would ideally be positioned between the seat back and the vibration source.

[0006] The lateral vibration isolators disclosed herein are particularly, though not exclusively, useful in cars, trucks, and vans. One general embodiment includes a vehicle seat with a first seat component; a second seat component rotatably coupled to the first seat component by a rotatable joint; and a laterally oriented vibration isolator positioned between the first and second seat components at the rotatable joint so as to inhibit transmission of vibrations from the first seat component to the second seat component through the rotatable joint.

[0007] Implementations may include one or more of the following features: In some embodiments, the first seating component is a seat pan or a seat frame. In some embodiments, the second seating component is a seat back. In some embodiments, the laterally oriented vibration isolator is a quasi-zero stiffness (QZS) vibration isolator. In some embodiments, the laterally oriented vibration isolator is rotatably coupled to the first seating component or the second seating component. In some embodiments, the laterally oriented vibration isolator further includes a threaded coupling having at least a portion of a bolt threaded therethrough, where rotation of the bolt through the threaded coupling compresses or decompresses the laterally oriented vibration isolator, thereby increasing or decreasing the preload force on the laterally oriented vibration isolator. In some embodiments, the preload force or degree of compression is selected such that the laterally oriented vibration isolator is within a quasi-zero stiffness range. In some embodiments, the laterally oriented vibration isolator is a first laterally oriented vibration isolator, and the vehicle seat further includes a second laterally oriented vibration isolator positioned between the first and second seat components at the rotatable joint. In some embodiments, the laterally oriented vibration isolator is a first laterally oriented vibration isolator, the rotatable joint is a first rotatable joint, and the vehicle seat further includes a second rotatable joint between the first and second seat components, and a second laterally oriented vibration isolator is positioned between the first and second seat components at the second rotatable joint, thereby inhibiting transmission of lateral vibrations from the first seat component to the second seat component through the second rotatable joint. In some embodiments, the vehicle seat further includes: a third laterally oriented vibration isolator positioned between the first seat component and the second seat component at the first rotatable joint; and a fourth laterally oriented vibration isolator positioned between the first seat component and the second seat component at the second rotatable joint.

[0008] One general embodiment includes a vehicle with a vehicle seat that includes: a seat base including a seat pan or seat frame; the seat frame; a seat back rotatably coupled to the seat pan or seat frame by a rotatable joint; and a vibration isolator positioned between the seat base and the seat back at the rotatable joint such that transmission of vibrations from the seat base to the seat back through the rotatable joint is inhibited.

[0009] Implementations may include one or more of the following features: In some embodiments, the vibration isolator is a quasi-zero stiffness (QZS) vibration isolator. In some embodiments, the vibration isolator is a quasi-zero stiffness (QZS) vibration isolator, where the vibration isolator further includes a threaded coupling having at least a portion of a bolt threaded therethrough, and rotation of the bolt through the threaded coupling compresses or decompresses the vibration isolator, thereby increasing or decreasing the preload force on the vibration isolator. In some embodiments, the preload force or compression is selected such that the vibration isolator is within a quasi-zero stiffness range. In some embodiments, the vibration isolator is a first vibration isolator, and the vehicle seat further includes a second vibration isolator positioned between the seat base and the seat back at a rotatable joint. In some embodiments, the vibration isolator is a first vibration isolator, and the vehicle seat further includes a second rotatable joint between the seat base and the seat back, where the second vibration isolator is positioned between the seat base and the seat back at the second rotatable joint, thereby reducing transmission of vibrations from the seat base to the seat back through the second rotatable joint. In some embodiments, the vehicle further includes a third vibration isolator positioned between the seat base and the seat back at the first rotatable joint; and a fourth vibration isolator positioned between the seat base and the seat back at the second rotatable joint.

[0010] One general embodiment includes a seat base including a seat pan or seat frame; a seat frame; a seat back rotatably coupled to the seat pan or seat frame by a rotatable joint; and a laterally oriented quasi-zero seatbelt positioned between the seat base and the seat back at the rotatable joint. Tsuyoshi and a bolt connecting the vibration isolator to the seat base or seat back, wherein the vibration isolator further includes a threaded connecting portion through which at least a portion of the bolt threads, and rotation of the bolt through the threaded connecting portion compresses or decompresses the vibration isolator, thereby increasing or decreasing the preload force on the laterally oriented vibration isolator.

[0011] This Summary is provided to introduce selected concepts in a simplified form that are further described below in the Detailed Description. This Summary is not intended to identify key features or essential features of the claimed subject matter, nor is it intended to limit the scope of the claimed subject matter. A more extensive presentation of the features, details, benefits, and advantages of the lateral vibration isolators defined in the claims is provided in the following description of various embodiments of the present disclosure and illustrated in the accompanying drawings.

[0012] Exemplary embodiments of the present disclosure will be described with reference to the accompanying drawings. [Brief explanation of the drawings]

[0013] [Figure 1] FIG. 1 is an exemplary representation of a conventional linear spring isolator according to an embodiment of the present disclosure. [Figure 2A] FIG. 2A is a perspective view of a ring-shaped or conical disk, disc spring, or disk spring washer according to an embodiment of the present disclosure. [Figure 2B] FIG. 2B is a cross-sectional side view of an exemplary quasi-zero stiffness (QZS) vibration isolator according to an embodiment of the present disclosure. [Figure 2C] FIG. 2C is a perspective view of an exemplary QZS vibration isolator according to an embodiment of the present disclosure. [Figure 3] FIG. 3 illustrates a performance graph of an exemplary linear spring isolator and an exemplary QZS isolator, according to an embodiment of the present disclosure. [Figure 4] FIG. 4 is a performance graph illustrating force versus displacement for five different exemplary QZS isolators, according to an embodiment of the present disclosure. [Figure 5A] FIG. 5A is a perspective view of an exemplary one-dimensional (1D) QZS vibration isolator measurement device according to an embodiment of the present disclosure. [Figure 5B] FIG. 5B is a performance graph illustrating the 1D vibration damping performance of two different types of isolators, according to an embodiment of the present disclosure. [Figure 6A] FIG. 6A is a perspective view of an exemplary two-dimensional (2D) QZS vibration isolator measurement device according to an embodiment of the present disclosure. [Figure 6B] FIG. 6B is a performance graph illustrating vibration suppression performance of the QZS isolator according to an embodiment of the present disclosure. [Figure 7] FIG. 7 is a perspective view of a vehicle seat with its wiring, cushioning, and upholstery removed, according to an embodiment of the present disclosure. [Figure 8A] FIG. 8A is a perspective view of a vehicle seat according to an embodiment of the present disclosure. [Figure 8B] FIG. 8B is a performance graph illustrating vibration suppression performance of the QZS isolator according to an embodiment of the present disclosure. [Figure 9] FIG. 9 is a side cross-sectional view of a seat back lateral vibration isolator mechanism in accordance with at least one embodiment of the present disclosure. [Figure 10] FIG. 10 is a front view of a vehicle seat back lateral vibration isolator mechanism in accordance with at least one embodiment of the present disclosure. [Figure 11] FIG. 11 is a perspective view of a vehicle seatback lateral vibration isolator mechanism in accordance with at least one embodiment of the present disclosure. DETAILED DESCRIPTION OF THE INVENTION

[0014] To reduce the transmission of vibration along any given axis, stacked disk isolators or quasi-zero stiffness (QZS) isolators can be utilized, which consist of a stack of flexible Belleville or disk spring washers arranged in a stack of alternating cones separated by ring-shaped spacers positioned on the inner or outer edges of the washers. By suitable selection of spring design parameters, such spring stacks can be designed to produce a quasi-zero / negative stiffness response to a range of forces applied to the spring stack (i.e., when subjected to forces within this design force range, the spring stack can deflect over a relatively wide range of values ​​in response to small or zero increases in the applied force). Under these conditions, the spring stack can deflect from a first element (e.g., a vehicle seat bottom, seat frame, or seatback hinge) to a second element (e.g., a vehicle seat frame). Sheet It has been discovered that the transmission of vibrations to the back can be eliminated or substantially attenuated.

[0015] In some cases, when a lateral QZS vibration isolator is positioned to isolate a seat back from vibrations originating within the seat pan or seat frame, the QZS isolator can be optimized when an axial preload force is applied to the spring stack sufficient to cause the stack to reach its quasi-zero / negative stiffness response range. In such a preload force configuration, the QZS vibration isolator is within its quasi-zero stiffness response range even when no external forces (e.g., vibration forces) are applied. Therefore, the greatest benefit of the QZS region can be applied to suppressing the transmission of vibrations from the seat bottom (e.g., seat pan or seat frame) to the seat back. The QZS vibration isolator would ideally be positioned between the seat back and the vibration source, for example, on the hinge connecting the seat back to the seat pan or seat frame. Because the vibration amplitude may be greater at the top of the seat back than at its base, any reduction in vibration at the bottom of the seat back will be felt more strongly, for example, at the occupant's head level.

[0016] The proposed arrangement helps improve vehicle seat comfort by reducing vibrations transmitted upward from the seat bottom into the seat back. This design offers an improvement over existing vehicle seats because it allows for a horizontal deflection range that does not generate any significant lateral forces. As a result, less vibration is transmitted between the seat base (e.g., seat pan and / or seat frame) and the seat back, thus providing a smoother ride for the occupant.

[0017] For the purposes of promoting an understanding of the principles of the present disclosure, reference will now be made to the embodiments in the drawings, and specific language will be used to describe the same. It will nevertheless be understood that no limitation on the scope of the present disclosure is intended. All alterations and further modifications to the described devices, systems, and methods, and any further applications of the principles of the present disclosure, as would normally occur to one skilled in the art to which the present disclosure pertains, are fully contemplated and are included within the present disclosure. In particular, it is fully contemplated that features, components, and / or steps described in connection with one embodiment can be combined with features, components, and / or steps described in connection with other embodiments of the present disclosure. However, for the sake of brevity, many iterations of these combinations will not be separately described.

[0018] These descriptions are provided for illustrative purposes only and should not be considered as limiting the scope of the lateral vibration isolators. Certain features may be added, deleted, or modified without departing from the spirit of the claimed subject matter.

[0019] FIG. 1 is an exemplary representation of a conventional linear spring isolator 100 according to an embodiment of the present disclosure. The linear spring isolator 100 includes a top mounting portion 110 and a bottom mounting portion 120 separated by a spring 130. The spring 130 may be, for example, a metal spring that deflects (e.g., compresses or expands) in a manner that is approximately linearly related to the amount of normal force applied to the isolator 100. In one example, the linear spring isolator 100 may be installed between a vehicle seat and a vehicle floor in an attempt to limit the transmission of vibrations from the floor to the seat. In such a use case, the top mounting portion 110 may be bolted to, for example, a seat frame, while the bottom mounting portion 120 may be bolted to, for example, the vehicle floor or the top of a slide rail to which the seat is mounted. Such an undamped linear spring isolator 100 provides only limited vibration isolation and limited lateral stability and lateral load capacity.

[0020] 2A is a perspective view of a ring-shaped or conical disk 230, also known as a Belleville spring or disk spring washer, according to an embodiment of the present disclosure. Disk 230 may be made of, for example, rubber or another resilient material that has the ability to bend and then return to its original shape. The disk's conical shape is formed because inner and outer edges 204 and 206 of disk 230 are vertically separated by a height H. Inner edge 204 forms a central opening 202 with a diameter D1, while outer edge 206 of disk 230 has a diameter D2. The material forming spring disk or washer 230 has a thickness T.

[0021] FIG. 2B illustrates an exemplary quasi-zero TsuyoshiFIG. 1 is a side cross-sectional view of a QZS vibration isolator 200. The QZS isolator 200 includes a plurality of ring-shaped or conical rubber discs 230, also known as Belleville springs, disc spring washers, or spring disc washers. The discs 230 are separated by inner spacers 210 coupled to the inner edge of each spring disc washer 230 or each pair of spring disc washers 230. The spring disc washers 230 are also separated by outer spacers 220 coupled to the outer edge of each spring disc washer 230. The discs or Belleville springs 230 are stacked such that when two discs 230 are vertically adjacent to one another, either their two outer edges 206 (see FIG. 1A ) are coupled to the same outer spacer 220 or their inner edges 204 (see FIG. 1A ) are coupled to the same inner spacer 210. Thus, the stack of disks or washers 230 forms a bellows shape that has the ability to compress vertically and then return to its original shape.

[0022] QZS vibration isolator 200 can include either an even or odd number of spring disc washers 230. Spring disc washers 230 may be coupled to spacers 210 and 220 using a friction fit or an adhesive bond, either or both of which may involve grooves, slots, or indentations, or any combination thereof, in either spacers 210, 220 or spring disc washers 230.

[0023] 2C is a perspective view of an exemplary QZS vibration isolator 200, according to an embodiment of the present disclosure. Visible are inner spacer 210, outer spacer 220, and disc spring washer 230.

[0024] FIG. 3 illustrates a performance graph 300 for an exemplary linear spring isolator 330 and an exemplary QZS isolator 340, according to an embodiment of the present disclosure. The linear spring isolator curve 330 shows a linear or approximately linear relationship between the applied force F and the resulting spring deflection x. The slope of this line is the spring constant k of the spring, such that F = kx. The QZS isolator curve 340 shows a more complex relationship between the applied normal force F and the resulting normal deflection or compression x. This force-deflection relationship includes a first approximately linear region 350 and a second approximately linear region 360 separated by a quasi-zero stiffness (QZS) region 370. Thus, the force-deflection relationship can be approximated as three straight line segments 355, 365, and 375.

[0025] Within the first approximately linear region 350, the slope of curve 340 may be approximated as F = k1x, producing a first line segment 355. For the QZS region, the slope may be approximated as zero, producing a second line segment 375. For the second approximately linear region 360, the slope of curve 340 may be approximated as F = K2x, producing a third line segment 365.

[0026] In the quasi-zero stiffness region 365 of the QZS isolator curve 340, it can be said that a small increase in the downward force F on the QZS isolator results in a disproportionately large increase in deflection x, or alternatively, that a large change in deflection x does not result in a significant change in the upward force F delivered by the isolator. As will be shown below, this force-deflection relationship 340 makes the QZS isolator more effective than a linear spring at damping or isolating vibrations.

[0027] 4 is a performance graph 400 illustrating force 310 versus displacement 320 for five different exemplary QZS isolators, namely, 410A (two disc spring washers), 410B (three disc spring washers), 410C (four disc spring washers), 410D (five disc spring washers), and 410E (six disc spring washers), according to an embodiment of the present disclosure. As shown in FIG. 3, the force-displacement curve for each QZS isolator includes a first approximately linear region 350, a quasi-zero stiffness (QZS) region 370, and a second approximately linear region 360. As can be seen from graph 400, the width or displacement of QZS area 370 (e.g., the number of millimeters of displacement allowed within the QZS area) increases with the number of disc spring washers, so that QZS isolator 410A with two disc spring washers has a QZS area that is approximately 1 mm wide, while QZS isolator 410E with six disc spring washers has a QZS area that is approximately 4 mm wide. Therefore, QZS isolators with more disc spring washers are better able to absorb movement at the bottom of the isolator (e.g., movement of the vehicle floor) without transmitting it to the top of the isolator (e.g., to the bottom of the vehicle seat). However, QZS isolators with more disc spring washers must be correspondingly taller, which may limit where they can be mounted and the applications in which they can be used. Taller QZS isolators also tend to be more costly due to the need for more material, and may have lower lateral stability and lower lateral load capacity than shorter QZS isolators. Therefore, taller QZS isolators may be more prone to buckling under lateral loads, and in this buckled state the QZS vibration isolators may be substantially less effective at isolating vibrations in both the longitudinal and lateral directions.

[0028] 5A is a perspective view of an exemplary one-dimensional (1D) QZS vibration isolator measurement setup according to an embodiment of the present disclosure. Visible is a proof mass 510 mounted to a vibration table 520 by a vibration isolator 550. For lateral and rotational stability during 1D vibration testing, the proof mass 510 includes three tubular channels 540 through which three shafts 530 pass.

[0029] FIG. 5B is a performance graph 500 illustrating the 1D vibration suppression performance of two different types of isolators in the test fixture of FIG. 5A according to an embodiment of the present disclosure. Graph 500 shows a curve of transmissibility 560 (e.g., measured in decibels, or dB) versus frequency 570 (measured in Hertz, or Hz) for linear spring isolator 580 and QZS isolator 590. This represents, for example, the degree to which vertical vibration of shaker table 520 (see FIG. 5A) is converted into vertical vibration of proof mass 510 (see FIG. 5A). A transmissibility of zero dB may represent complete transmission of vibration through isolator 550 (see FIG. 5A), such that vibration of the shaker table causes equal vibration of the proof mass at that particular frequency. A transmissibility greater than 0 dB may represent amplification by the isolator, such that vibration of the shaker table results in greater or more powerful vibration of the proof mass at that particular frequency. A transmissibility of less than 0 dB may represent vibration attenuation by the isolator such that vibration of the shaker table results in smaller or less powerful vibration of the proof mass at that particular frequency. Generally, values ​​less than 0 dB are desirable at all frequencies, and especially at higher frequencies.

[0030] As can be seen, linear spring isolator curve 580 exhibits a sharp peak 585 at approximately 12 Hz, which is believed to represent the resonant frequency of the spring, possibly causing a transmissibility of more than +30 dB (e.g., vibrations 100 times greater than those observed at 5 Hz and 15 Hz). The linear spring isolator curve does not drop below 0 dB until the vibration frequency exceeds 20 Hz. In contrast, QZS isolator curve 590 does not exhibit any sharp peaks, but rather drops below 0 dB at a vibration frequency of approximately 10 Hz and remains below zero throughout the remainder of the curve. QZS isolator curve 590 is similarly lower at all points than linear spring isolator curve 580, indicating that the QZS isolator is better at suppressing vertical vibrations (or, alternatively, is worse at transmitting such vibrations) than the linear spring isolator.

[0031] 6A is a perspective view of an exemplary two-dimensional (2D) QZS vibration isolator measurement setup according to an embodiment of the present disclosure. Viewed is a vertical proof mass 620 fixedly mounted to a horizontal proof mass 610, which is itself mounted to a vibration table 520 by a pair of QZS vibration isolators 200. The effectiveness of the QZS isolators 200 can be assessed, for example, by measuring vibrations at the top of the vertical proof mass 620 and comparing it to vibrations measured at the surface of the vibration table 520. Vibration of the vibration table 520 results in rocking of the proof masses 610 and 620, which in turn results in torques and lateral forces on the QZS isolators.

[0032] FIG. 6B is a performance graph 600 illustrating the vibration suppression performance of the QZS isolators in the test setup of FIG. 6A , according to an embodiment of the present disclosure. Graph 600 shows a curve of transmissibility 560 (e.g., measured in decibels, or dB) versus frequency 570 (measured in Hertz, or Hz) for a non-insulated mass 680 and a QZS isolated mass 690. This represents the extent to which, for example, vertical vibrations of shaking table 520 (see FIG. 6A ) are translated into vertical and horizontal vibrations of the top of vertical proof mass 620 (see FIG. 6A ) through, for example, lateral oscillations of the lower proof mass due to uneven compression of QZS isolators 200. A transmissibility of zero dB may represent perfect transmission of vibrations through QZS isolators 200 (see FIG. 6A ), such that vibrations of the shaking table cause equal vibrations of the top of the vertical mass at that particular frequency. A transmissibility greater than 0 dB may represent amplification by the isolators and / or proof masses, such that vibration of the shaker table results in a greater or more powerful vibration of the top of the vertical proof mass at that particular frequency. A transmissibility less than 0 dB may represent vibration attenuation by the isolators, such that vibration of the shaker table results in a less or less powerful vibration of the top of the vertical proof mass at that particular frequency. Generally, values ​​less than 0 dB are desirable at all frequencies, and especially at higher frequencies.

[0033] As can be seen, if the test mass were mounted directly to the shaker table without any vibration isolation, the test mass would amplify the vibrations of the shaker table by 10 to 15 dB across all frequencies of interest, as represented by curve 680. QZS isolation curve 690 shows a larger amplification of 15 to 20 dB between 5 Hz and 10 Hz. However, at all frequencies of interest above 10 Hz, the amplification is less than that of curve 680, and is less than zero (indicating a net damping of vibration) at all frequencies of interest above 20 Hz. This demonstrates that the QZS isolators are effective in reducing the vibrations of the 2D shaker.

[0034] It is pointed out that 2D vibrations can induce lateral forces on the seat.

[0035] 7 is a perspective view of a vehicle seat 700 with its wiring, cushioning, and upholstery removed, according to an embodiment of the present disclosure. The vehicle seat 700 includes a seat pan or seat cushion pan 710, a seat back or seat back frame 720, and a recliner 730 for adjusting the angle between the seat pan 710 and the seat back 720. The seat 700 also includes a seat frame 750 that is attached to the vehicle floor 740 using two slide rails 760 that allow the seat 700 to slide rearward and forward relative to the floor 740.

[0036] 8A is a perspective view of a vehicle seat 700 according to an embodiment of the present disclosure. The vehicle seat 700 includes a seat back 720 coupled to a seat pan 710, which is coupled to a seat frame 750. The seat frame 750 is coupled to a plurality of QZS vibration isolators 200, which are themselves coupled to slide rails 760 coupled to the vehicle floor. The coupling may be, for example, through welding, bolts, screws, rivets, solder, adhesive, or other means known in the art. The QZS isolators 200 are configured to reduce the transmission of vibrations between the vehicle floor 740 and the seat 700.

[0037] FIG. 8B is a performance graph 800 illustrating the vibration suppression performance of QZS isolator 200 of FIG. 8A according to an embodiment of the present disclosure. Graph 800 shows a curve of transmissibility 560 (e.g., measured in decibels, or dB) versus frequency 570 (measured in Hertz, or Hz) for non-insulated mass 810 and QZS isolating mass 820. This represents the extent to which, for example, vibrations of floor 740 (see FIG. 8A) are translated into vibrations of the top of seat back 720 (see FIG. 8A) through lateral rocking of the lower proof mass due to, for example, uneven compression of QZS isolator 200 (see FIG. 8A). A transmissibility of zero dB may represent perfect transmission of vibrations through QZS isolator 200 (see FIG. 6A), such that floor vibrations cause equal vibrations of the top of the seat back at that particular frequency. A transmissibility greater than 0 dB may represent amplification by the seat structure and / or isolators, such that floor vibrations result in larger or more powerful vibrations at the top of the seat at that particular frequency. A transmissibility less than 0 dB may represent vibration attenuation by the isolators, such that floor vibrations result in smaller or less powerful vibrations at the top of the seat back at that particular frequency. Generally, values ​​less than 0 dB are desirable at all frequencies, and especially at higher frequencies.

[0038] As can be seen, both QZS isolation curve 820 and unisolated curve 810 exhibit amplitude spikes at low frequencies. Spike 815 on unisolated curve 810 occurs at 10 Hz and has a maximum value of approximately 30 dB. Spike 825 on QZS isolation curve 820 is actually larger than spike 815 on curve 810, with a peak value of approximately 37 dB, indicating even greater amplification of floor vibrations. However, this spike occurs at a lower frequency (i.e., 7 Hz for spike 825 compared to 10 Hz for spike 815), and therefore may result in less overall discomfort for the seated user. Notably, QZS isolation curve 820 exhibits 10 dB lower amplitude (e.g., 10 times less vibration transmission) than unisolated curve 810 across most frequencies of interest, from 9 Hz to 47 Hz. QZS isolation curve 820 is approximately equal to unisolated curve 810 at 17 Hz and 47-50 Hz. The total area under curve 820 is significantly less than the total area under curve 810, indicating a lower overall vibration transmissibility between the vehicle floor and the top of the seat back. Thus, one skilled in the art will recognize that the QZS isolator can be effective in reducing vibrations in a vehicle seat, generally resulting in a more comfortable ride for the seat occupant.

[0039] It is noted that vibrations of the vehicle floor and / or vehicle seat can induce lateral forces on the seat. As discussed above, there is a need for a lateral QZS isolation device capable of reducing lateral vibrations of the seat back.

[0040] 9 is a side cross-sectional view of a seat back lateral vibration isolator mechanism 900 according to at least one embodiment of the present disclosure. The seat back or seat back frame 720 is subjected to a lateral vibration force 930 that is transmitted through attachment points 940 into the seat back 720 itself near the bottom of the seat back 720. Because the seat back forms a lever arm or inverted pendulum, oscillatory motion near the bottom of the seat back can result in greater oscillatory motion near the top of the seat back. Such lateral vibrations (e.g., vibrations occurring along the lateral or side-to-side axis of the vehicle or vehicle seat) can also occur unevenly, causing the seat back 720 to exhibit a lateral rocking motion that generates a torque force 920.

[0041] A spring stack or QZS vibration isolator 200 may be assembled on each side of the portion of the seat back 720 at the attachment point 940 where the seat back 720 connects to the seat pan 710 or seat frame 750. Each spring stack or QZS 200 may be positioned between the attachment point 940 on the seat pan 710 or seat frame 750 and that portion of the seat back. Thus, the attachment point 940 where the seat back 720 connects to the seat pan 710 or seat frame 750 is supported between the spring stacks 200 on either side.

[0042] Because the seat back 720 contacts the seat pan 710 and / or seat frame 750 at attachment points 940, vibrations from the seat pan 710 and / or seat frame 750 are transmitted through the attachment points 940. Therefore, assembling spring stacks or vibration isolators 200 on either side of the attachment points 940 helps to isolate the seat back 720 from torque forces 920 and lateral vibration forces 930 transmitted between the seat pan 710 or seat frame 750 and the seat back 720.

[0043] Although FIG. 9 shows a total of four spring stacks or QZS vibration isolators 200, one skilled in the art will recognize that the seat back 720 can be attached to the seat pan 710 and / or seat frame 750 by other arrangements and other numbers of spring stacks or QZS vibration isolators 200, including one, two, three, five, six or more spring stacks or QZS isolators 200.

[0044] FIG. 10 is a front view of a vehicle seat back lateral vibration isolation mechanism 1000 in accordance with at least one embodiment of the present disclosure. In the non-limiting example shown in FIG. 10 , a portion of a seat back frame 720 is attached to a seat frame 750 by two bolts 1010. Each bolt 1010 threads from an attachment point 1040 in the seat frame 750 to an attachment point 1050 on a spring stack or QZS vibration isolator 200. The spring stack or isolator is then coupled to attachment point 940 on the seat back frame 720. Such coupling may be with screws, welds, pins, rivets, additional bolts, or other means known in the art.

[0045] To compress the spring stack or QZS vibration isolator 200 with a preload force, bolts 1010 may engage complementary threaded elements on attachment points 1050 of the spring stack or QZS vibration isolator 200. Rotation of bolts 1010 can axially compress or decompress the spring stack or QZS vibration isolator 200, depending on the direction of rotation. Each spring stack or QZS vibration isolator can be preloaded with its respective bolt to the point where the stack provides a quasi-zero / negative stiffness response even when no external vibration forces are applied. Thus, when a vibration force is applied, the vibration force encounters the spring stack or QZS isolator 200 in the QZS region where vibration isolation is most effective.

[0046] FIG. 11 is a perspective view of a vehicle seat back lateral vibration isolator mechanism 1100 in accordance with at least one embodiment of the present disclosure. Similar to FIG. 7, FIG. 11 illustrates a vehicle seat including a seat pan or seat cushion pan 710, a seat back 720, a recliner mechanism 730, a seat frame 750, and slide rails 760. In this embodiment, the recliner mechanism 730 is a powered axle that connects the seat frame 750 to the seat back 720. Rotation of the recliner mechanism 730 tilts or raises the seat back depending on the direction of rotation. Because a power recliner serves as the connection between the seat frame 750 and the seat back 720 in this embodiment, a single spring stack or QZS isolator 200 is installed on each side of the recliner mechanism 730, such that the seat back 720 can rise and recline normally, but the seat frame 750 is connected to the seat back 720 only through the spring stacks 200. In some embodiments, the spring stack 200 is fixedly coupled to the seat back 720 and recliner mechanism 730 and rotationally coupled to the seat frame 750, such that the spring stack 200 rotates along with the recliner mechanism as the seat tilts or rises. In other embodiments, the spring stack is fixedly coupled to the seat frame 750 and rotationally coupled to the recliner mechanism 730 and / or the seat back, such that the spring stack 200 does not rotate as the seat back 720 tilts and rises. In still other embodiments, the spring stack 200 is free to rotate independently of both the seat back 720 and the seat frame 750 or seat pan 710.

[0047] Either or both of the fixed or rotary joints may include bolts that may thread into threaded connections on the spring stack 200 such that the preload force on the spring stack 200 is adjusted by adjusting the bolts as described above.

[0048] As one skilled in the art will readily recognize after becoming familiar with the teachings herein, the lateral vibration isolators of the present disclosure advantageously provide the ability to isolate or damp lateral vibrations in a vehicle seat back. In some cases, the preload force or deflection is dynamically adjusted based on the weight applied to the QZS isolator. It should be noted that the above-described examples are provided for illustrative purposes and are not intended to be limiting. Other devices and / or device configurations may be utilized to perform the operations described herein. Many variations on the above-described examples and embodiments are possible. Depending on the implementation, the location or orientation may differ from that shown in the present invention. For example, while the components of the QZS vibration isolator may be illustrated and described herein as circular, conical, or cylindrical, other shapes with non-circular (e.g., elliptical, polygonal, etc.) cross-sections may alternatively or additionally be used for one or more components. The techniques described herein may be used in other types of vehicles, including campers, trailer homes, commercial tow vehicles, motorcycles, off-road vehicles, aircraft, and watercraft. The exact configuration of the QZS vibration isolators can be selected to optimize performance for the vibration frequencies and amplitudes expected for such vehicles. The vibration isolator preload force mechanism can be used for lateral vibration isolation between fixed vehicle components and other vehicle components, including, but not limited to, seats, engines, engine components, batteries, cargo holds, cargo platforms, wheels, bumpers, and baggage bins.

[0049] Accordingly, the logical operations making up the embodiments of the technology described in this invention are referred to variously as operations, steps, objects, elements, components or modules, and it should be understood that they may be arranged or performed in any order unless expressly claimed otherwise or unless a particular order is inherently required by claim language.

[0050] All directional references, such as upper, lower, medial, lateral, upward, downward, left, right, lateral, center, front, rear, top, bottom, upward, downward, vertical, horizontal, clockwise, counterclockwise, proximal, and distal, are used for identification purposes only to aid the reader in understanding the claimed subject matter and are not intended to create limitations on the location, orientation, or use of the lateral vibration isolators in particular. References to connections, such as attached, coupled, connected, and joined, should be interpreted broadly and, unless otherwise indicated, may include intermediate members between elements and relative movement between elements. As such, connected references do not necessarily imply that two elements are directly connected and in a fixed relationship to each other. The term "or" should be interpreted to mean "and / or" rather than "exclusive or." The term "comprising" does not exclude other elements or steps, and the indefinite articles "a" or "an" do not exclude a plurality. Unless otherwise indicated in the claims, the values ​​listed are to be construed as merely exemplary and not as limiting.

[0051] The above specification, examples, and data provide a complete description of the structure and use of exemplary embodiments of lateral vibration isolators as defined in the claims. While various embodiments of the claimed subject matter have been described above with a certain degree of specificity, or with reference to one or more individual embodiments, it is believed that those skilled in the art could make many modifications to the disclosed embodiments without departing from the spirit or scope of the claimed subject matter.

[0052] Further embodiments are contemplated. All matter contained in the above description and shown in the accompanying drawings is to be interpreted as merely illustrative of particular embodiments, and not as limiting. Changes in detail or structure may be made without departing from the essential elements of the subject matter defined in the following claims.

Claims

1. a first sheet component; a second seat component rotatably coupled to the first seat component by a rotatable joint; a laterally oriented vibration isolator positioned at the rotatable joint between the first seat component and the second seat component to inhibit transmission of vibrations through the rotatable joint from the first seat component to the second seat component; a bolt connecting the laterally oriented vibration isolator to the first seat component or the second seat component; Including, the laterally oriented vibration isolator further comprising a threaded connection portion through which at least a portion of the bolt threads; rotation of the bolt through the threaded connection compresses or decompresses the laterally oriented vibration isolator to increase or decrease a preload force on the laterally oriented vibration isolator.

2. The vehicle seat of claim 1 , wherein the first seat component is a seat pan or a seat frame.

3. 10. The vehicle seat of claim 1, wherein the second seat component is a seat back.

4. 2. The vehicle seat of claim 1, wherein the laterally oriented vibration isolator is a near-zero stiffness (QZS) vibration isolator.

5. The vehicle seat of claim 1 , wherein the laterally oriented vibration isolator is rotatably coupled to the first seat component or the second seat component.

6. 10. The vehicle seat of claim 1, wherein the preload force or compression is selected such that the laterally oriented vibration isolator is within a near-zero stiffness range.

7. 2. The vehicle seat of claim 1, wherein the laterally oriented vibration isolator is a first laterally oriented vibration isolator, and the vehicle seat further includes a second laterally oriented vibration isolator positioned between the first seat component and the second seat component at the rotatable joint.

8. 2. The vehicle seat of claim 1, wherein the laterally oriented vibration isolator is a first laterally oriented vibration isolator, the rotatable joint is a first rotatable joint, the vehicle seat further includes a second rotatable joint between the first seat component and the second seat component, and a second laterally oriented vibration isolator is positioned at the second rotatable joint between the first seat component and the second seat component, and transmission of lateral vibrations from the first seat component to the second seat component through the second rotatable joint is suppressed.

9. a third laterally oriented vibration isolator positioned between the first seat component and the second seat component at the first rotatable joint; a fourth laterally oriented vibration isolator positioned between the first seat component and the second seat component at the second rotatable joint; 9. The vehicle seat of claim 8, further comprising:

10. a seat base including a seat pan or seat frame; a seat frame; a seat back rotatably coupled to the seat pan or the seat frame by a rotatable joint; a vibration isolator positioned at the rotatable joint between the seat base and the seat back, to suppress transmission of vibrations from the seat base to the seat back through the rotatable joint; a vehicle seat including: Including, further comprising a bolt connecting the vibration isolator to the seat base or the seat back; the vibration isolator is a quasi-zero stiffness (QZS) vibration isolator; the vibration isolator further includes a threaded connection portion through which at least a portion of the bolt threads; Rotation of the bolt through the threaded connection compresses or decompresses the vibration isolator, increasing or decreasing the preload force on the vibration isolator.

11. The vehicle of claim 10 , wherein the vibration isolator is a quasi-zero stiffness (QZS) vibration isolator.

12. The vehicle of claim 10 , wherein the preload force or compression is selected so that the vibration isolator is in a near-zero stiffness range.

13. 11. The vehicle of claim 10, wherein the vibration isolator is a first vibration isolator, and the vehicle seat further includes a second vibration isolator positioned between the seat base and the seat back at the rotatable joint.

14. 11. The vehicle of claim 10, wherein the vibration isolator is a first vibration isolator, and the vehicle seat further includes a second rotatable joint between the seat base and the seat back, wherein a second vibration isolator is positioned between the seat base and the seat back at the second rotatable joint, and transmission of vibrations from the seat base to the seat back through the second rotatable joint is suppressed.

15. The rotatable joint is a first rotatable joint, and a third vibration isolator is positioned at the first rotatable joint between the seat base and the seat back; a fourth vibration isolator positioned between the seat base and the seat back at the second rotatable joint; 15. The vehicle of claim 14, further comprising:

16. Vehicles and a seat base including a seat pan or seat frame; a seat frame; a seat back rotatably coupled to the seat pan or the seat frame by a rotatable joint; a laterally oriented near-zero stiffness vibration isolator positioned between the seat base and the seat back at the rotatable joint; a bolt connecting the vibration isolator to the seat base or the seat back; Including, the vibration isolator further includes a threaded connection portion through which at least a portion of the bolt threads; Rotation of the bolt through the threaded connection compresses or decompresses the vibration isolator, increasing or decreasing the preload force on the laterally oriented vibration isolator. A seat and A system including:

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