CN113700795A - Vibration isolation method and device for light truck cab with quasi-zero stiffness characteristic - Google Patents
Vibration isolation method and device for light truck cab with quasi-zero stiffness characteristic Download PDFInfo
- Publication number
- CN113700795A CN113700795A CN202111035587.6A CN202111035587A CN113700795A CN 113700795 A CN113700795 A CN 113700795A CN 202111035587 A CN202111035587 A CN 202111035587A CN 113700795 A CN113700795 A CN 113700795A
- Authority
- CN
- China
- Prior art keywords
- quasi
- vibration isolation
- zero
- spring
- light truck
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000002955 isolation Methods 0.000 title claims abstract description 40
- 239000000725 suspension Substances 0.000 claims abstract description 31
- 238000006073 displacement reaction Methods 0.000 claims abstract description 19
- 238000000034 method Methods 0.000 claims abstract description 6
- 150000001875 compounds Chemical class 0.000 claims description 3
- 238000009795 derivation Methods 0.000 claims description 2
- 230000000694 effects Effects 0.000 abstract description 4
- 230000005284 excitation Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
- F16F15/067—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only wound springs
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/15—Vehicle, aircraft or watercraft design
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation
Abstract
The invention relates to a vibration isolation method and device for a light truck cab with quasi-zero rigidity characteristic, and belongs to the technical field of vibration isolation. In order to solve the problems that the conventional vibration isolation method has a shaking phenomenon in a low-speed area of a truck and the vibration isolation effect is not obvious, the vibration isolation method and the vibration isolation device for the light truck cab with the quasi-zero rigidity characteristic are provided, and the vibration isolation method and the vibration isolation device can perform low-frequency vibration isolation. According to the method, a horizontal elastic mechanism, a rotating mechanism suspended in front of a light truck cab and a supporting mechanism suspended behind the light truck cab are added to the rear suspension position of the light truck cab to form a quasi-zero rigidity suspension system, and when the system is in a non-horizontal balance position, the horizontal elastic mechanism and the rotating mechanism form a mechanism with negative rigidity characteristics and are connected with the supporting mechanism in parallel to form the suspension system with the quasi-zero rigidity characteristics. By utilizing a parallel connection method of a positive stiffness system and a negative stiffness system, a force-displacement relation and a stiffness-displacement relation of the system and a precondition for meeting the quasi-zero stiffness characteristic are deduced through mechanical analysis.
Description
Technical Field
The invention relates to a vibration isolation method and device, in particular to a vibration isolation method and device for a light truck cab with quasi-zero rigidity characteristic, and belongs to the technical field of vibration isolation.
Background
Cab shaking is a major problem that customers now complain about during truck use. The reasons for this are mainly: due to the uneven road surface and the system vibrations caused by the dynamic imbalance of the tires (what is the dynamic imbalance of the tires), when the vibration frequency coincides with a certain natural frequency in the truck system, the system resonates, thereby generating cab vibrations.
At present, a front suspension of a common cab of a light truck cab adopts a rotating mechanism on the vibration isolation design, and a rear suspension adopts a rubber supporting mechanism. The vibration isolation design of the light truck cab is simplified into a vibration mechanism consisting of a rocker and a spring, and the problem of pitching modal vibration easily occurs in the structural form. The rigid body mode of a common cab is within 10HZ, and according to the vibration isolation theory, only when the ratio of the excitation frequency to the natural frequency of a vibration isolation system is greater than that
The system will only attenuate the input displacement. Due to the fact that the excitation frequency is low in the light truck low-speed area, the vibration isolation method is used for enabling the truck to frequently shake in the low-speed area, and the vibration isolation effect is not obvious.
Disclosure of Invention
The invention aims to solve the problems that the conventional vibration isolation method has a shaking phenomenon in a low-speed area of a truck and the vibration isolation effect is not obvious, provides a light truck cab vibration isolation method and device with quasi-zero rigidity characteristic and capable of isolating vibration at low frequency, and belongs to the technical field of vibration isolation.
The vibration isolation method for the light truck cab is realized by the following technical scheme:
a vibration isolation method for a light truck cab is characterized in that: according to the method, a horizontal elastic mechanism, a rotating mechanism suspended in front of a light truck cab and a supporting mechanism suspended behind the light truck cab are added to the rear suspension position of the light truck cab to form a quasi-zero rigidity suspension system, and when the system is in a non-horizontal balance position, the horizontal elastic mechanism and the rotating mechanism form a mechanism with negative rigidity characteristics and are connected with the supporting mechanism in parallel to form the suspension system with the quasi-zero rigidity characteristics.
Preferably, the suspension system with the quasi-zero stiffness characteristic of the vibration isolation method for the light truck cab utilizes the geometric nonlinear negative stiffness characteristic and the adjustable type of the geometric parameters thereof, is connected with the load through the vertical elastic element and the horizontal elastic element-connecting rod, and realizes the characteristic of accurate quasi-zero stiffness characteristic in the design range through parameter configuration.
Preferably, the suspension system comprises a rotating mechanism simplified as a rocker, a supporting mechanism simplified as a spring A and a horizontal elastic mechanism simplified as a spring B, wherein the spring A is vertically installed at the tail end of the rocker, the spring B is horizontally installed at the tail end of the rocker, and the spring A and the spring B are installed at the same end of the rocker.
Preferably, when the system deviates from the equilibrium position, the horizontal force is kept balanced according to the relation of the stress, and the following results are obtained:
in the formula, F1 is the pressure on the rotating mechanism, namely the rocker, and F2 is the pressure on the horizontal elastic mechanism, namely the spring B;
the vertical force Fh by F1 and F2 is:
Fh＝F1 sinα+F2 sinβ (2)
by substituting formula (1) for formula (2), a compound of formula (2) can be obtained
Fh＝F2 sinβ+F2 cosαtanβ (3)
The length of the rocker is a, the height of the rocker is x, the horizontal distance from the supporting mechanism to the horizontal elastic mechanism is d, and the formula (3) can be converted into
The restoring force F2 of spring B is
Where d0 is the amount the spring B is pre-compressed in the horizontal position.
Thus, the force in the vertical direction of the system
F＝k1x-Fh (6)
From the formulae (4), (5) and (6),
obtaining a force-displacement characteristic curve according to the formula (7);
performing derivation operation on the displacement x on the formula (7) to obtain a relational expression between the system rigidity K and the displacement x, referring to the formula (8), and obtaining a rigidity-displacement curve according to the formula (8);
in order to ensure that the stiffness of the vibration isolation system at the equilibrium position is zero, formula (8) is substituted with x being 0 and K being 0, and the precondition that the system satisfies the quasi-zero stiffness characteristic at the equilibrium position is as follows:
positive stiffness system: refers to a system where the force increases with increasing displacement.
Negative stiffness system: refers to a system in which the force is continuously reduced as the displacement increases.
Quasi-zero stiffness system: the system is a rigidity system with the rigidity close to zero near the balance, and the natural frequency of the system close to zero near the balance position, so that the low-frequency vibration isolation of the system is realized.
According to the vibration isolation method for the light truck cab, a force-displacement relation and a rigidity-displacement relation of a system and a precondition that the quasi-zero rigidity characteristic is met are deduced through mechanical analysis by using a parallel connection method of a positive rigidity system and a negative rigidity system; the rigidity of the system near the balance is close to zero, when the system is in a horizontal balance position, the system supporting force is provided by the spring A, the spring B is in a compressed state, when the system deviates from the balance position, the spring B and the connecting rod in the compressed state form a mechanism with negative rigidity characteristics, and the mechanism is connected with the spring A in parallel to form a suspension system with quasi-zero rigidity characteristics.
Drawings
FIG. 1: the suspension system of the existing vibration isolation method for the light truck cab;
FIG. 2: the suspension system after the vibration isolation method for the light truck cab is simplified;
FIG. 3: FIG. 2 is a force diagram of the suspension system when it is out of equilibrium;
FIG. 4: a quasi-zero stiffness suspension force-displacement curve;
FIG. 5: a quasi-zero stiffness suspension stiffness-displacement curve;
FIG. 6: and adopting a vibration curve of the driving end and the driven end after the quasi-zero stiffness system.
Detailed Description
In order to make the technical means, the creation characteristics, the achievement purposes and the effects of the invention easy to understand, the invention is further described with the specific embodiments.
In the description of the present invention, it should be noted that the terms "upper", "lower", "inner", "outer", "front", "rear", "both ends", "one end", "the other end", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "disposed," "connected," and the like are to be construed broadly, such as "connected," which may be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood according to specific situations by those of ordinary skill in the art.
A horizontal elastic mechanism, a rotating mechanism suspended in front of a light truck cab and a supporting mechanism suspended behind the light truck cab are additionally arranged at a rear suspension position of the light truck cab to form a quasi-zero rigidity suspension system, and when the system is in a non-horizontal balance position, the horizontal elastic mechanism and the rotating mechanism form a mechanism with negative rigidity characteristics and are connected with the supporting mechanism in parallel to form the suspension system with the quasi-zero rigidity characteristics.
A suspension system with quasi-zero stiffness characteristic of a light truck cab vibration isolation method is disclosed, as shown in figure 2, the characteristic of accurate quasi-zero stiffness characteristic in a design range is realized by utilizing the geometric nonlinear negative stiffness characteristic and the adjustable type of the geometric parameters thereof, connecting with a load through a vertical elastic element and a horizontal elastic element-connecting rod and configuring parameters.
The suspension system comprises a rotating mechanism simplified into a rocker, a supporting mechanism simplified into a spring A and a horizontal elastic mechanism simplified into a spring B, wherein the spring A is vertically installed at the tail end of the rocker, the spring B is horizontally installed at the tail end of the rocker, and the spring A and the spring B are installed at the same end of the rocker.
When the system deviates from the equilibrium position, as shown in fig. 3, the horizontal force is kept balanced according to the relation of the force, and the following can be obtained:
in the formula, F1 is the pressure on the rotating mechanism, namely the rocker, and F2 is the pressure on the horizontal elastic mechanism, namely the spring B;
the vertical force Fh by F1 and F2 is:
Fh＝F1 sinα+F2 sinβ (2)
by substituting formula (1) for formula (2), a compound of formula (2) can be obtained
Fh＝F2 sinβ+F2 cosαtanβ (3)
The length of the rocker is a, the height of the rocker is x, the horizontal distance from the supporting mechanism to the horizontal elastic mechanism is d, and the formula (3) can be converted into
The restoring force F2 of spring B is
Where d0 is the amount the spring B is pre-compressed in the horizontal position.
Thus, the force in the vertical direction of the system
F＝k1x-Fh (6)
From the formulae (4), (5) and (6),
the force-displacement characteristic curve can be obtained from equation (7), as shown in fig. 4. The vibration isolation system has the characteristics of quasi-zero rigidity, the rigidity at the balance position is zero, and the rigidity value in a certain interval is close to zero, so that the system can keep a certain force value around the balance position unchanged, the rigidity of the system is close to zero in a certain range around the balance position, and the isolation of low-frequency vibration is realized.
The derivative operation of the displacement x is performed on the equation (7), and the relationship between the system stiffness K and the displacement x is obtained, and the stiffness-displacement curve is obtained from the equation (8) with reference to the equation (8), as shown in fig. 5.
In order to ensure that the stiffness of the vibration isolation system at the equilibrium position is zero, formula (8) is substituted with x being 0 and K being 0, and the precondition that the system satisfies the quasi-zero stiffness characteristic at the equilibrium position is as follows:
a quasi-zero stiffness system is designed according to the principle, the parameters of the quasi-zero stiffness system are shown in the following table 1, and after the quasi-zero stiffness system is applied, the vibration of the main and driven ends of the rear suspension of the cab is measured and is shown in fig. 6. It can be seen from the figure that the quasi-zero stiffness suspension system can solve the problem of low-frequency vibration isolation of suspension.
TABLE 1 QUASI-ZERO RIGIDITY VIBRATION ISOLATION SYSTEM PARAMETER TABLE
| K1(N/mm) | K2(N/mm) | a(mm) | b(mm) | d(mm) | d0(mm) |
| 400 | 792 | 2000 | 2020 | 10 | 5 |
The foregoing shows and describes the general principles and broad features of the present invention and advantages thereof. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are described in the specification and illustrated only to illustrate the principle of the present invention, but that various changes and modifications may be made therein without departing from the spirit and scope of the present invention, which fall within the scope of the invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (4)
1. A vibration isolation method for a light truck cab is characterized in that: according to the method, a horizontal elastic mechanism, a rotating mechanism suspended in front of a light truck cab and a supporting mechanism suspended behind the light truck cab are added to the rear suspension position of the light truck cab to form a quasi-zero rigidity suspension system, and when the system is in a non-horizontal balance position, the horizontal elastic mechanism and the rotating mechanism form a mechanism with negative rigidity characteristics and are connected with the supporting mechanism in parallel to form the suspension system with the quasi-zero rigidity characteristics.
2. A suspension system having quasi-zero stiffness characteristics based on the method of claim 1, wherein: the characteristic of accurate quasi-zero degree rigidity characteristic in the design range is realized by utilizing the adjustable type of the geometric non-linear negative rigidity characteristic and the geometric parameters thereof and connecting the vertical elastic element, the horizontal elastic element and the connecting rod with the load through parameter configuration.
3. A suspension system having quasi-zero stiffness characteristics as claimed in claim 2, wherein: the suspension system comprises a rotating mechanism simplified into a rocker, a supporting mechanism simplified into a spring A and a horizontal elastic mechanism simplified into a spring B, wherein the spring A is vertically installed at the tail end of the rocker, the spring B is horizontally installed at the tail end of the rocker, and the spring A and the spring B are installed at the same end of the rocker.
4. A suspension system having quasi-zero stiffness characteristics as claimed in claim 3, wherein: when the system deviates from the balance position, the horizontal force keeps balance according to the relation of the stress, and the following results are obtained:
in the formula, F1 is the pressure on the rotating mechanism, namely the rocker, and F2 is the pressure on the horizontal elastic mechanism, namely the spring B;
the vertical force Fh by F1 and F2 is:
Fh＝F1 sinα+F2 sinβ (2)
by substituting formula (1) for formula (2), a compound of formula (2) can be obtained
Fh＝F2 sinβ+F2 cosαtanβ (3)
The length of the rocker is a, the height of the rocker is x, the horizontal distance from the supporting mechanism to the horizontal elastic mechanism is d, and the formula (3) can be converted into
The restoring force F2 of spring B is
Where d0 is the amount of precompression for spring B in the horizontal position;
thus, the force in the vertical direction of the system
F＝k1x-Fh (6)
From the formulae (4), (5) and (6),
the formula (7) is subjected to a derivation operation of the displacement x to obtain a relational expression between the system stiffness K and the displacement x,
in order to ensure that the stiffness of the vibration isolation system at the equilibrium position is zero, formula (8) is substituted with x being 0 and K being 0, and the precondition that the system satisfies the quasi-zero stiffness characteristic at the equilibrium position is as follows:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111035587.6A CN113700795A (en) | 2021-09-03 | 2021-09-03 | Vibration isolation method and device for light truck cab with quasi-zero stiffness characteristic |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111035587.6A CN113700795A (en) | 2021-09-03 | 2021-09-03 | Vibration isolation method and device for light truck cab with quasi-zero stiffness characteristic |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113700795A true CN113700795A (en) | 2021-11-26 |
Family
ID=78659996
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111035587.6A Pending CN113700795A (en) | 2021-09-03 | 2021-09-03 | Vibration isolation method and device for light truck cab with quasi-zero stiffness characteristic |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113700795A (en) |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB0402625D0 (en) * | 2004-02-06 | 2004-03-10 | Boc Group Plc | Vibration damper |
| US20150369331A1 (en) * | 2012-12-12 | 2015-12-24 | Shanghai Micro Electronics Equipment Co., Ltd. | Negative stiffness system for gravity compensation of micropositioner |
| CN105864339A (en) * | 2016-06-01 | 2016-08-17 | 福州大学 | Quasi-zero stiffness vibration isolator applicable to isolation of micro-amplitude and low-frequency vibration and realization method of quasi-zero stiffness vibration isolator |
| CN106402267A (en) * | 2016-05-23 | 2017-02-15 | 福州大学 | Extension type quasi-zero stiffness vibration isolator and implementation method thereof |
| CN106542009A (en) * | 2015-09-21 | 2017-03-29 | 湖北港汉电子科技有限公司 | Full floating commercial-vehicle cab front-suspension system |
| CN106542010A (en) * | 2015-09-21 | 2017-03-29 | 湖北港汉电子科技有限公司 | Full floating Ride Comfort of Commercial Vehicle Cab Suspension System |
| CN108313139A (en) * | 2018-03-15 | 2018-07-24 | 中国第汽车股份有限公司 | Truck cap suspension system |
| CN109532589A (en) * | 2018-12-21 | 2019-03-29 | 安徽工程大学 | Double-layer vibration isolating seat |
| CN210191656U (en) * | 2019-06-25 | 2020-03-27 | 一汽解放汽车有限公司 | Commercial truck cab rear suspension system and vehicle |
| CN112178121A (en) * | 2020-10-09 | 2021-01-05 | 北京理工大学 | Quasi-zero stiffness vibration isolator with inclined compression rod |
| CN212556546U (en) * | 2020-07-08 | 2021-02-19 | 扬州市宇联车身有限公司 | Novel cab suspension structure with transverse reduction function |
-
2021
- 2021-09-03 CN CN202111035587.6A patent/CN113700795A/en active Pending
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB0402625D0 (en) * | 2004-02-06 | 2004-03-10 | Boc Group Plc | Vibration damper |
| US20150369331A1 (en) * | 2012-12-12 | 2015-12-24 | Shanghai Micro Electronics Equipment Co., Ltd. | Negative stiffness system for gravity compensation of micropositioner |
| CN106542009A (en) * | 2015-09-21 | 2017-03-29 | 湖北港汉电子科技有限公司 | Full floating commercial-vehicle cab front-suspension system |
| CN106542010A (en) * | 2015-09-21 | 2017-03-29 | 湖北港汉电子科技有限公司 | Full floating Ride Comfort of Commercial Vehicle Cab Suspension System |
| CN106402267A (en) * | 2016-05-23 | 2017-02-15 | 福州大学 | Extension type quasi-zero stiffness vibration isolator and implementation method thereof |
| CN105864339A (en) * | 2016-06-01 | 2016-08-17 | 福州大学 | Quasi-zero stiffness vibration isolator applicable to isolation of micro-amplitude and low-frequency vibration and realization method of quasi-zero stiffness vibration isolator |
| CN108313139A (en) * | 2018-03-15 | 2018-07-24 | 中国第汽车股份有限公司 | Truck cap suspension system |
| CN109532589A (en) * | 2018-12-21 | 2019-03-29 | 安徽工程大学 | Double-layer vibration isolating seat |
| CN210191656U (en) * | 2019-06-25 | 2020-03-27 | 一汽解放汽车有限公司 | Commercial truck cab rear suspension system and vehicle |
| CN212556546U (en) * | 2020-07-08 | 2021-02-19 | 扬州市宇联车身有限公司 | Novel cab suspension structure with transverse reduction function |
| CN112178121A (en) * | 2020-10-09 | 2021-01-05 | 北京理工大学 | Quasi-zero stiffness vibration isolator with inclined compression rod |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US10208825B2 (en) | Anti-vibration device for vehicle | |
| CN201747842U (en) | Single barrel type oil and gas spring | |
| CN110439946A (en) | Equipment quasi-zero stiffness vibration isolators under a kind of railway vehicle truck | |
| CN109058377B (en) | Quasi-zero rigidity shock absorber for high-speed train floor | |
| CN106274919A (en) | Express locomotive suspension device of motor | |
| CN110239332B (en) | Self-adjusting rigidity and damping power assembly suspension | |
| US20110121500A1 (en) | Vibration absorber for a vehicle suspension spring | |
| CN113700795A (en) | Vibration isolation method and device for light truck cab with quasi-zero stiffness characteristic | |
| CN107458528A (en) | Front wheel of electric motorcar support frame | |
| US20060000658A1 (en) | Engine subframe mounting arrangement | |
| JPS6339458Y2 (en) | ||
| CN202251640U (en) | Novel air suspension | |
| CN207157399U (en) | A kind of front wheel of electric motorcar support frame | |
| CN206306757U (en) | Air suspension system | |
| CN204020474U (en) | Passenger car air-conditioner compressor erecting frame and passenger vehicle | |
| CN207349333U (en) | A kind of sleeved rubber mounting structure | |
| CN206201896U (en) | A kind of commercial car rubber suspension of good stability | |
| CN105003592B (en) | Rear axle power bump leveller | |
| CN214331697U (en) | Concrete pumping pipeline compound damping support | |
| CN114688201A (en) | Quasi-zero stiffness vibration isolation system adopting diaphragm disc spring and air suspension frame in series connection | |
| CN204605499U (en) | A kind of auxiliary engine side direction damping and stabilizing device | |
| EP0178934B1 (en) | A mounting arrangement for a vehicle engine | |
| CN209901150U (en) | Dispersing machine | |
| CN217623035U (en) | Mounting structure of air suspension system bumper shock absorber and vehicle thereof | |
| CN111799931A (en) | Shock attenuation diesel generator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20211126 |
|
| RJ01 | Rejection of invention patent application after publication |