CN204512264U - Vibration isolator and compressor system comprising same - Google Patents
Vibration isolator and compressor system comprising same Download PDFInfo
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- CN204512264U CN204512264U CN201520135415.XU CN201520135415U CN204512264U CN 204512264 U CN204512264 U CN 204512264U CN 201520135415 U CN201520135415 U CN 201520135415U CN 204512264 U CN204512264 U CN 204512264U
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Abstract
The utility model relates to a vibration isolator, this vibration isolator have first surface and the second surface relative with the first surface along axial direction. The vibration isolator includes: a solid portion extending from the first surface to the second surface in the axial direction; and an air gap portion adjacent to the solid portion and extending from the first surface to the second surface in the axial direction, at least one air gap being provided in the air gap portion. The at least one air gap is configured to: the non-closing in the first operating condition causes the isolator pad to have a first stiffness, and the at least partial closing in the second operating condition causes the isolator pad to have a second stiffness greater than the first stiffness. The utility model discloses still relate to a compressor system including this vibration isolator.
Description
Technical field
The utility model relates to a kind of vibration isolator, particularly a kind of for compressor being mounted to supporting structure to reduce the vibration isolator vibrated.The utility model also relates to a kind of compressor assembly comprising this vibration isolator, especially, for the air-conditioning system of train.
Background technique
The content of this part provide only the background information relevant to the disclosure, and it may not form prior art.
Compressor is installed on the support structure by leg usually.When compressor normally runs (steady working condition), compressor self can produce vibration, and thus by leg by vibration passing to supporting structure.In order to vibration damping, the leg of compressor is installed on the support structure via vibration isolator.The vibration isolation capability of vibration isolator depends primarily on its rigidity.Generally speaking, the rigidity of vibration isolator is less, and vibration isolator more advantageously can reduce the vibration being passed to supporting structure that compressor self produces.
But in some cases, the traffic tool (such as, automobile, truck, train etc.) that compressor is arranged on motion are gone up and are applied in its air-conditioning system.Such as, train start and stop, acceleration, slow down or suffer other impact (impact operating mode) time, therefore the leg that this impact can be passed to compressor via vibration isolator from train (that is, for installing the supporting structure of compressor) is also passed to compressor.In this case, compressor is tending towards producing larger displacement, produces larger vibration conversely to train.Therefore, the easy fatigue damage of the vibration isolator be usually made up of rubber, that is, shorten working life.When impacting, it is intended that vibration isolator has comparatively large rigidity.Like this, the rigidity of vibration isolator is larger, and vibration isolator more can the displacement of advantageously limit compression machine.
For this reason, International Electronical Commission (IEC) (International Electro TechnicalCommission, referred to as IEC) has formulated shock test standard, to carry out Laboratory Evaluation based on the applied environment of harshness to product at Design Stage.In this way, can guarantee that vibration that compressor operationally produces can not affect the performance of vehicle (such as, train), such as, the performance of noise, vibration and sound vibration roughness (Noise, Vibration and harshness, referred to as NVH).
Conventional vibration isolator substantially in cylindric, and is made up of rubber material.In order to meet afore mentioned rules, MANUFACTURER, by selecting the size of different rubber materials and/or design vibration isolator, makes vibration isolator have certain rigidity.Once vibration isolator is made, its rigidity substantially no longer changes during use, that is, vibration isolator has substantially invariable rigidity.The vibration isolator with constant rate often can not meet the requirement impacting operating mode when the requirement meeting steady working condition, or often can not meet the requirement of steady working condition when the requirement of satisfied impact operating mode.
Therefore, a kind of vibration isolator that simultaneously can meet the requirement of steady working condition and impact operating mode is needed.
Model utility content
An object of the present utility model is to provide a kind of vibration isolator that simultaneously can meet the requirement of steady working condition and impact operating mode.
Another object of the present utility model is to provide a kind of lower-cost vibration isolator.
Another object of the present utility model is to provide a kind of vibration isolator of simplified processing process.
Another object of the present utility model is to provide a kind of compressor assembly comprising this vibration isolator.
One or more in above-mentioned purpose can be realized by following proposal: a kind of vibration isolator, this vibration isolator in axial direction has first surface and the second surface relative with first surface.This vibration isolator comprises: the entity portion in axial direction extending to second surface from first surface; And contiguous entity portion and in axial direction extend to the air gap portion of second surface from first surface, in air gap portion, be provided with at least one air gap.At least one air gap is configured to: closedly under the first operating mode make vibration isolator have the first rigidity, and closedly at least in part under the second operating mode makes vibration isolator have second rigidity larger than the first rigidity.
According to vibration isolator of the present utility model owing to being provided with air gap, and air gap can be opened under different operating mode or close, and therefore can change effective carrying cross sectional area of vibration isolator, thus changes the rigidity of vibration isolator.Such as, under stationary conditions, the air gap of vibration isolator is opened and has less rigidity with the vibration of absorption equipment (such as, compressor) self generation better; Under impact operating mode, the air gap of vibration isolator closes and has the rigidity of increase thus improve the ability of resistance to deformation.
On the other hand, can open and close according to the air gap of vibration isolator of the present utility model, therefore suction (or breathing) effect that air gap produces when open and close can change the damping of vibration isolator to a certain extent, can improve the damping capacity of vibration isolator thus further.
Alternatively, according in vibration isolator of the present utility model, air gap portion is arranged on the outside in entity portion along the horizontal direction in direction perpendicular to axial direction.Air gap extends from the outer side surface in air gap portion towards entity portion.Like this, air gap can be communicated with well with ambient atmosphere.
Alternatively, according in vibration isolator of the present utility model, air gap portion also can be arranged on the inner side in entity portion along the horizontal direction in direction perpendicular to axial direction.In addition, vibration isolator can also comprise the interstice portion that transversely direction is arranged on real portion outside, and interstice portion comprises at least one air gap.Like this, according to embody rule demand, two air gap portions can be set to obtain better variation rigidity effect.
Alternatively, vibration isolator can comprise multiple air gap portion and multiple entity portion.Multiple air gap portion and multiple entity portion alternately arrange around the central axis of vibration isolator.
Alternatively, when the inside of vibration isolator is provided with air gap, vibration isolator can also comprise the vent for being communicated with air gap and ambient atmosphere.
For the ease of install vibration isolator, vibration isolator can also comprise the centre being arranged on vibration isolator for through fastening piece to install the mounting hole of vibration isolator.
Further, air gap can circumferentially extend by direction continuously or intermittently, or continuously or intermittently extension in a spiral form in the axial direction, or extends in the form of a step in circumferential direction.
Alternatively, vibration isolator can comprise multiple air gap, and multiple air gap has identical size and structure.Like this, can simplified processing process, reduce costs.Such as, the structure of simplification can be had for the manufacture of the mould of vibration isolator.Or vibration isolator can have symplex structure, such as to improve the stressing conditions of vibration isolator.
Alternatively, vibration isolator can comprise multiple air gap, and multiple air gap is configured so that: at least two air gaps a) in multiple air gap have the different degree of depth in a lateral direction in direction perpendicular to axial direction; And/or at least two air gaps b) in multiple air gap have different height in the axial direction.Such structure, closes or opens when air gap can be made different, therefore can obtain stepped stiffness variation.
Preferably, the height on the axial direction of air gap is in the scope of 0.5mm to 3mm.
Alternatively, vibration isolator can comprise multiple air gap, and multiple air gap at least one direction in the horizontal direction in axial direction, circumferential direction and direction perpendicular to axial direction is arranged alignedly, arranges abreast or arrange alternately.
Preferably, vibration isolator is cylindric, and/or vibration isolator is made up of rubber material.
Alternatively, vibration isolator can form, or can be formed by the thin slice of superposition different size.When the air gap negligible amounts of vibration isolator, it can be favourable for utilizing the mode of superposition thin slice to form vibration isolator.Like this, manufacture cost can be reduced.
According to another aspect of the present utility model, relate to a kind of compressor assembly comprising above-mentioned vibration isolator.Particularly, this compressor assembly can comprise compressor and above-mentioned vibration isolator, and wherein, the supporting leg of compressor is mounted on the support structure via vibration isolator.
Alternatively, a few vibration isolator can be respectively provided in the upper side and lower side of supporting leg.The vibration isolator being positioned at the upper side and lower side of supporting leg can have different structure and/or different size.
Preferably, via the fastening piece inserted in the mounting hole of vibration isolator and sleeve, supporting leg is mounted to supporting structure, wherein, sleeve to be arranged between fastening piece and vibration isolator and to be configured to can control when supporting leg being mounted to supporting structure the preload of vibration isolator.
Above-mentioned compressor system can be the air-conditioning system for the traffic tool, and/or compressor can be horizontal compressor.
By below in conjunction with accompanying drawing, the description that principle of the present utility model is described by way of example, other aspects of the present utility model and advantage will become obvious.
Accompanying drawing explanation
By the description referring to accompanying drawing, the feature and advantage of one or several mode of execution of the present utility model will become easier to understand, wherein:
Figure 1A is the schematic perspective view of the assembling according to vibration isolator of the present utility model and compressor;
Figure 1B is the schematic side view of Figure 1A;
Fig. 2 A is the schematic front view of the vibration isolator of Figure 1B and the amplification of compressor leg;
Fig. 2 B is the generalized section of the vibration isolator of Fig. 2 A;
Fig. 3 A is the schematic perspective view of the vibration isolator according to the utility model first mode of execution;
Fig. 3 B is the generalized section of the vibration isolator of Fig. 3 A;
Fig. 4 A is the schematic perspective view of vibration isolator when air gap closes according to the utility model mode of execution;
Fig. 4 B is the generalized section of the vibration isolator of Fig. 4 A;
Fig. 5 is the generalized section of the vibration isolator according to the utility model second mode of execution;
Fig. 6 is the generalized section of the vibration isolator according to the utility model the 3rd mode of execution;
Fig. 7 A is the schematic perspective view of the vibration isolator according to the utility model the 4th mode of execution;
Fig. 7 B is the generalized section of the vibration isolator of Fig. 7 A;
Fig. 8 A is the schematic perspective view of the vibration isolator according to the utility model the 5th mode of execution;
Fig. 8 B is the generalized section of the vibration isolator of Fig. 8 A;
Fig. 9 A is the schematic perspective view of the vibration isolator according to the utility model the 6th mode of execution;
Fig. 9 B is the generalized section of the vibration isolator of Fig. 9 A;
Figure 10 is the schematic perspective view of the vibration isolator according to the utility model the 7th mode of execution;
Figure 11 A is the schematic perspective view of the vibration isolator according to the utility model the 8th mode of execution;
Figure 11 B is the generalized section of the vibration isolator of Figure 11 A;
Figure 12 is the generalized section of the vibration isolator according to the utility model the 9th mode of execution; And
Figure 13 is the schematic diagram changed along with operating mode according to axial displacement and the rigidity of vibration isolator of the present utility model.
Embodiment
Be only exemplary to the description of the various mode of execution of the utility model below, and be never the restriction to the utility model and application or usage.Adopt similar reference character to represent similar parts in various figures, therefore the structure of similar parts is by no longer repeated description.
The noun of locality mentioned in this article, such as " upper and lower, left and right ", refer to orientation observed on accompanying drawing, unless separately had explicitly bright herein.
Usually, in order to reduce the vibration of machine or equipment (such as, compressor), this machine or equipment are mounted to pedestal (also referred to as " supporting structure ") via vibration isolator.Vibration isolator can reduce the vibration produced by machine or equipment self, the impact that the vibration reducing machine or equipment thus causes supporting structure.On the other hand, the impact that the impact etc. that vibration isolator also can reduce to carry out self supporting structure causes machine or equipment.
The vibration isolating effect (or effectiveness in vibration suppression) of vibration isolator depends primarily on its rigidity and damping.Rigidity refers to that material or structure resist the ability of resiliently deformable when stressed, with area and length or height correlation.That is, area is larger, and rigidity is larger; And length or highly larger, then rigidity is less.In this article, inventor enables same vibration isolator be adapted to different operating mode based on this principle by changing the rigidity of vibration isolator and/or damping.
Vibration isolator is made up of rubber material usually.The rigidity estimation equation of the rubber vibration insulating pad of substantial cylindrical is as follows:
The estimation equation of compression stiffness:
The estimation equation of shearing rigidity:
Wherein, Kc is compression stiffness; G is Young's modulus (relevant to material self attributes); A is the area in cylindrical cross-section (effective bearing cross-section, that is, the cross section perpendicular to loading direction of vibration isolator); H is the height (that is, along the size that vibration isolator axially records) of rubber vibration insulating pad; S is the shape factor on loaded surfaces/unloading surface; Ks is shearing rigidity; And d is diameter.
The height of vibration isolator depends primarily on applicable cases and installing space.Therefore, after vibration isolator is made, the boundary dimension of vibration isolator is determined, therefore, can think that the height of vibration isolator is substantially invariable.
Therefore, from formula above, the compression stiffness of rubber vibration insulating pad and shearing rigidity are all directly proportional to cylindrical cross-section area A, that is, cylindrical cross-section area A is larger, then the rigidity of rubber vibration insulating pad is larger; And cylindrical cross-section area A is less, then the rigidity of rubber vibration insulating pad is less.
According to this vibrational theory, present inventor has made the vibration isolator of variable rigidity between the spreadable life.Such as, when compressor smooth running, according to vibration isolator of the present utility model, there is less rigidity, effectively can reduce the less vibration that compressor self produces.When compressor is subject to impacting, the effective cross-sectional area according to vibration isolator of the present utility model can be increased, thus increase rigidity, effectively can reduce the impact impacted and compressor is caused thus.
To be described in detail according to vibration isolator of the present utility model for compressor see accompanying drawing below.But, it will be understood by those skilled in the art that and can be applied on any vibrative equipment or machine according to vibration isolator of the present utility model, and be not limited to compressor.In addition, for ease of describing, describe the system of installing compressor herein for train, in this case, supporting structure described herein can be train vehicle body or other structural members.It is to be understood, however, that compressor can be mounted in any other suitable system via according to vibration isolator of the present utility model.
See Figure 1A, Figure 1B, Fig. 2 A and Fig. 2 B, show the compressor assembly installed via vibration isolator.Illustrated compressor assembly comprises compressor 20, vibration isolator 10 and the supporting structure 50 (see Fig. 2 A and 2B) for supports compressor.The leg 22 of compressor 20 is mounted to supporting structure 50 via vibration isolator 10.
In illustrated embodiment, compressor 20 in general cylindrical shape, and is horizontal compressor.Compressor 20 is supported by two legs 22 and is mounted in supporting structure 50 via vibration isolator 10.See Fig. 2 A and 2B, a vibration isolator 10 can be respectively set in the upper side and lower side of leg 22.The substantial middle place of vibration isolator 10 is provided with through hole, to be inserted by bolt 30 in through hole and to be connected to supporting structure 50, thus compressor 20 being connected to supporting structure 50.
In said system, vibration isolator 10 is arranged between compressor 20 and supporting structure 50, can reduce by the rigidity of vibration isolator 10 and damping the vibration being passed to supporting structure 50 from compressor 20, also can reduce the external load such as impacted being passed to compressor from supporting structure 50 simultaneously.
When steady working condition, expect the vibration that vibration isolator has less rigidity and produces effectively to absorb compressor, and when impacting operating mode, then expect vibration isolator have comparatively large rigidity effectively to resist impulsive load.But conventional vibration isolator is substantially determined due to its cross section and height equidimension and is had substantially invariable rigidity after formation, is difficult to the actual demand meeting steady working condition and impact operating mode.
The utility model has been made based on this.Comprise entity portion according to vibration isolator of the present utility model and there is the air gap portion of at least one air gap.Under stationary conditions, the air gap in air gap portion does not close.Now, the rigidity of vibration isolator depends primarily on the cross sectional area in entity portion.Thus, vibration isolator has less rigidity, can effectively absorb the vibration produced by compressor, thus reduces the vibration being passed to train.
On the other hand, under impact operating mode, the air gap in air gap portion closes.Now, the rigidity of vibration isolator depends primarily on the cross sectional area in entity portion and air gap portion, that is, the rigidity of vibration isolator becomes large.Therefore, air gap portion can resist impulsive load together with entity portion, effectively prevents compressor generation larger displacement thus.
Be described according to the mode of execution of vibration isolator of the present utility model below with reference to accompanying drawings.It should be understood that the mode of execution illustrating and describe illustrates the utility model in an illustrative manner herein, is not whole mode of execution of the present utility model, neither to restriction of the present utility model.
First mode of execution > of < vibration isolator
See Fig. 3 A and Fig. 3 B, show the first mode of execution according to vibration isolator of the present utility model.According to the vibration isolator 10A of the utility model first mode of execution roughly in cylindric, and there is end face 12, bottom surface 14 and column outer side surface 16.Be provided with vertically at the substantial middle place of vibration isolator 10A and pass vibration isolator 10A to be mounted to the mounting hole 13 in supporting structure for bolt 30.Axis described herein is consistent with the direction of transmitted load between compressor and supporting structure.
See Fig. 3 B, vibration isolator 10A is included in the entity portion 110 of the radial outside of mounting hole 13 and is positioned at the air gap portion 150 of radial outside in entity portion 110.For convenience of describing, schematically show the interface between entity portion 110 and air gap portion 150 with dotted line P.Entity portion 110 and air gap portion 150 can form.Entity portion described herein refers to part solid on axial direction, and air gap portion then refers to the part being provided with air gap.In the illustrated embodiment, the air gap portion 150 of vibration isolator comprises from outer side surface 16 to entity portion 110 and along the circumferential direction extend three air gaps 15.That is, air gap 15 does not have not radially (or, horizontal direction) extend through whole vibration isolator 10A.Air gap 15 has annular upper face 152, ring-type lower surface 154 and internal face 156, wherein, internal face 156 towards entity portion 110 radial direction away from outer side surface 16.Air gap 15 is communicated with ambient atmosphere by the opening on outer side surface 16, is thus conducive to air gap 15 and returns to open mode rapidly after impulsive load.
Alternatively, air gap 15 is arranged equally spacedly along the axis of vibration isolator.In this first mode of execution, air gap 15 has identical axial height (that is, vertically from the height of upper surface 152 to lower surface 154) and identical radial depth (that is, radially from the degree of depth of outer side surface 16 to internal face 156).
Height on the axial direction of air gap 15 can in the scope of 0.5mm to 3mm.Via when installing compressor according to vibration isolator of the present utility model, certain precompression (preload) is applied to vibration isolator, make the axial height of air gap 15 can in the scope of 0.1mm to 2mm.In order to set this precompression better, can sleeve 40 (see Fig. 2 B) be set between the fastening piece of such as bolt 30 and vibration isolator.Such as, the precompression that can fastening piece be regulated to apply vibration isolator by the height arranging sleeve 40.
Under stationary conditions, compressor is less than 0.1mm usually because vibrating the displacement caused.Therefore, under stationary conditions, air gap 15 does not close.That is, the upper surface 152 of air gap 15 keeps being separated a segment distance with lower surface 154.Now, the rigidity of vibration isolator depends primarily on the circular cross-sectional area A1 in entity portion 110, and therefore the rigidity of vibration isolator is less, effectively can absorb the vibration that compressor self produces.
In addition, inventor also finds: under impact operating mode, sometimes may cause compressor displacement number millimeter in the axial direction.Be arranged so that air gap is closed when impacting operating mode according to vibration isolator of the present utility model.That is, the upper surface 152 of air gap 15 and lower surface 154 can be superimposed together at least in part.As shown in Figure 4 A and 4 B shown in FIG., the upper surface 152 of air gap 15 and lower surface 154 are almost superimposed together completely.Now, the rigidity of vibration isolator depends on the circular cross-sectional area A1 in entity the portion 110 and circular cross-sectional area A2 in air gap portion 150, thereby increases the rigidity of vibration isolator.That is, entity portion 110 and the air gap portion 150 of vibration isolator resist impulsive load all effectively, prevent compressor from after being impacted, larger displacement occurring.
Opening or closing by air gap 15, can change the effective cross-sectional area according to vibration isolator 10 of the present utility model, correspondingly can change its rigidity, makes vibration isolator 10 can either be adapted to steady working condition thus and can adapt to again impact operating mode.In addition, under impact operating mode, add the rigidity of vibration isolator 10A due to the closed of air gap 15 and limit the displacement of compressor 20, protecting compressor 20 and connecting pipeline thereof etc. to a certain extent, and the working life of vibration isolator 15 can be extended.
Air gap 15 has air suction (or breathing) effect in the process of folding, therefore also can improve the damping of vibration isolator 10 to a certain extent, be conducive to further carrying out vibration damping to compressor 20.
In addition, in the illustrated embodiment, fillet part 18 can be set between end face 12 and outer side surface 16, to facilitate the installation and location etc. of vibration isolator 10A.Those skilled in the art, it is to be appreciated that according to embody rule situation, also can arrange fillet part 18 between outer side surface 16 and bottom surface 14.In addition, the form structure of vibration isolator correspondingly can be changed according to coordinating the structure of the structural member installed with vibration isolator.
Second mode of execution > of < vibration isolator
See Fig. 5, show the vibration isolator 10B according to the second mode of execution of the present utility model.Second mode of execution and the difference of the first mode of execution of vibration isolator are that the radial depth of air gap is different.As shown in Figure 5, air gap portion comprises from outer side surface 16 to entity portion and along the circumferential direction extend three air gaps 15A, 15B and 15C.Air gap 15A, 15B and 15C along vibration isolator axial order arrange and there is radial depth d1, d2 and d3 respectively, wherein, radial depth d1, d2 and d3 shorten successively.The radial depth d1 of air gap 15A is the longest, that is, the internal face 156A of air gap 15A is near mounting hole 13 and entity portion.The radial depth d3 of air gap 15C is the shortest, that is, the internal face 156C of air gap 15C is farthest away from mounting hole 13 and entity portion.In the radial depth d2 of the air gap 15B scope between d1 and d3, that is, the internal face 156B of air gap 15B is in radial directions between internal face 156A and 156C.
For the vibration isolator 10B according to the utility model second mode of execution, air gap 15A, 15B and 15C can not simultaneously close.Such as, air gap 15A, 15B and 15C can close successively according to the increase of impulsive load.Or, each radial depth of air gap 15A, 15B and 15C can be set according to the distribution situation of load on vibration isolator.
The part that second mode of execution of vibration isolator is identical with the first mode of execution is not described in detail.
3rd mode of execution > of < vibration isolator
See Fig. 6, show the vibration isolator 10C according to the 3rd mode of execution of the present utility model.3rd mode of execution and the difference of the first mode of execution of vibration isolator are that the axial height of air gap is different.As shown in Figure 6, air gap portion comprises from outer side surface 16 to entity portion and along the circumferential direction extend three air gap 15A ', 15B ' and 15C '.Air gap 15A ', 15B ' and 15C ' along vibration isolator axial order arrange and there is axial height h1, h2 and h3 respectively, wherein, axial height h1, h2 and h3 increase successively.The axial height h1 of air gap 15A ' is minimum.The axial height h3 of air gap 15C ' is maximum.In the axial height h2 of the air gap 15B ' scope between h1 and h3.
For the vibration isolator 10C according to the utility model the 3rd mode of execution, air gap 15A ', 15B ' and 15C ' can not simultaneously close.Such as, air gap 15A ', 15B ' and 15C ' can close successively according to the increase of impulsive load.Or, each axial height of air gap 15A, 15B and 15C can be set according to the distribution situation of load on vibration isolator.
The part that 3rd mode of execution of vibration isolator is identical with the first mode of execution is not described in detail.
4th mode of execution > of < vibration isolator
See Fig. 7 A and Fig. 7 B, show the vibration isolator 10D according to the 4th mode of execution of the present utility model.The difference of the vibration isolator 10D of the 4th mode of execution and the vibration isolator 10A of the first mode of execution is, the radial outside of entity portion 110 in air gap portion 150 and air gap portion 150 comprises four air gaps 15.Vibration isolator 10D according to the 4th mode of execution is radially inwardly disposed with entity portion 110, air gap portion 150 and mounting hole 13.The air gap 15 in air gap portion 150 is communicated with mounting hole 13, and therefore, air gap 15 can communicate with ambient atmosphere via mounting hole 13.
It should be understood that the quantity of air gap 15 can change according to embody rule situation, be not limited to concrete example described herein.
The part that 4th mode of execution of vibration isolator is identical with the first mode of execution is not described in detail.
5th mode of execution > of < vibration isolator
See Fig. 8 A and Fig. 8 B, show the vibration isolator 10E according to the 5th mode of execution of the present utility model.The difference of the vibration isolator 10E of the 5th mode of execution and the vibration isolator 10A of the first mode of execution is, each air gap 15 is along the circumferential direction arranged discontinuously.As shown in Figure 8 B, spacer portion 112 is provided with between two along the circumferential direction adjacent air gaps 15.In the illustrated embodiment, between adjacent two spacer portion 112, three air gaps 15 are in axial direction provided with abreast.In addition, at vibration isolator circumferentially, be provided with by four isolated four air gaps 15 of spacer portion 112.It should be understood that the quantity of spacer portion 112 and the quantity of air gap 15 can change according to embody rule situation.
In the illustrated embodiment, entity portion 110 (that is, the dash area in Fig. 8 B) comprises ring-type solid section and the spacer portion 112 of contiguous mounting hole 13.Air gap portion 150 is the part being provided with air gap 15 of vibration isolator.The air gap 15 being along the circumferential direction positioned at spacer portion 112 both sides can be arranged alignedly, or can arrange alternately.Be understandable that, the quantity of the air gap 15 between two adjacent spacer portion 112 can be different.
The part that 5th mode of execution of vibration isolator is identical with the first mode of execution is not described in detail.
6th mode of execution > of < vibration isolator
See Fig. 9 A and Fig. 9 B, show the vibration isolator 10F according to the 6th mode of execution of the present utility model.The difference of the vibration isolator 10F of the 6th mode of execution and the vibration isolator 10E of the 5th mode of execution is, air gap 15 extends to the inwall 132 of mounting hole 13 from the outer side surface 16 of vibration isolator 10F.Like this, entity portion 110 is made up of spacer portion 112.Spacer portion 112 and air gap 15 are along the circumferential direction arranged alternately.In other words, entity portion 110 along the circumferential direction can be arranged alternately with air gap portion 150.
The part no longer repeated description that 6th mode of execution is similar to the 5th mode of execution.
7th mode of execution > of < vibration isolator
See Figure 10, show the vibration isolator 10G according to the 7th mode of execution of the present utility model.The difference of the vibration isolator 10G of the 7th mode of execution and the vibration isolator 10A of the first mode of execution is, air gap 15 in stepped form, and is provided with two air gaps along the circumferential direction extended 15 in the axial direction abreast.Particularly, for each air gap 15, it extends certain distance after along the circumferential direction extending certain distance vertically, forms the form of step thus.Each air gap 15 can change according to embody rule situation in the quantity of the whole step circumferentially formed.
The part no longer repeated description that 7th mode of execution is similar to the first mode of execution.
8th mode of execution > of < vibration isolator
See Figure 11 A and Figure 11 B, show the vibration isolator 10H according to the 8th mode of execution of the present utility model.The difference of the vibration isolator 10H of the 8th mode of execution and the vibration isolator 10D of the 4th mode of execution is, the radial outside in entity portion 110 is also provided with interstice portion 160.For ease of describing, in this embodiment, air gap portion 150 is defined as the first air gap portion 150.
As shown in the figure, entity portion 110 is between the first air gap portion 150 and interstice portion 160.In Figure 11 B, schematically show the interface between the first air gap portion 150 and entity portion 110 with dotted line P1, and schematically show the interface between entity portion 110 and interstice portion 160 with dotted line P2.First air gap portion 150 is at the substantial middle place of vibration isolator 10H, and the air gap 15 in the first air gap portion 150 communicates with ambient atmosphere via mounting hole 13.Interstice portion 160 is at the radial outside of vibration isolator 10H, and the air gap 15 in interstice portion 160 extends from the outer side surface 16 of vibration isolator 10H towards entity portion 110, that is, the opening of air gap 15 is arranged on outer side surface 16, makes air gap 15 communicate with ambient atmosphere thus.
The air gap 15 in the first air gap portion 150 can be aimed in radial directions with the air gap 15 in interstice portion 160, or can interlaced arrangement.Be understandable that, the air gap 15 in the first air gap portion 150 can be different in quantity, size and/or configuration aspects from the air gap 15 in interstice portion 160.
The part no longer repeated description that 8th mode of execution is similar to the 4th mode of execution.
9th mode of execution > of < vibration isolator
See Figure 12, show the vibration isolator 10I according to the 9th mode of execution of the present utility model.The difference of the vibration isolator 10I of the 9th mode of execution and the vibration isolator 10D of the 4th mode of execution is, vibration isolator 10I does not arrange the mounting hole 13 passed for bolt at substantial middle place, but is connected to supporting structure by other means.
In vibration isolator 10I, be provided with vent 19 and communicate with ambient atmosphere to make air gap 15.In the shown embodiment, vent 19 is arranged on the substantial middle place of vibration isolator 10I and extends through vibration isolator 10I from air gap 15 vertically.It is to be understood, however, that the structure of vent 19 is not limited to illustrated example, but can be any structure, as long as air gap 15 can be made to communicate with ambient atmosphere.
For vibration isolator 10I, such as, by being fixedly attached in supporting structure the bottom surface of vibration isolator 10I, vibration isolator 10I can be connected to supporting structure, or, by the component of the outer side surface for fixing vibration isolator 10I, vibration isolator 10I can be connected to supporting structure.That is, vibration isolator can be connected to supporting structure by other modes except mounting hole 13 and bolt 30.
The part no longer repeated description that 9th mode of execution is similar to the 4th mode of execution.
Other modification > of <
Although be described in detail the some mode of executions according to vibration isolator of the present utility model above, but, be understood that, described mode of execution is only a part for the utility model mode of execution, its object is only used to the utility model is described, instead of to of the present utility model exhaustive.Above-mentioned mode of execution can also have a lot of modification and the feature of above-mentioned vibration isolator can mutually combine to form other mode of execution in reconcilable situation.
Such as, air gap 15 can in axial direction extend in spiral form.Although the vibration isolator illustrated herein and illustrate 10 is for roughly cylindric, it is to be understood, however, that according to embody rule situation, vibration isolator 10 can be any other suitable shape.
In addition, although the mode of execution illustrating herein and illustrate is integrated vibration isolator 10, but vibration isolator 10 also can be formed in other any suitable modes.Such as, vibration isolator 10 by the different thin slice of diameter or can be formed by stacking perpendicular to the thin slice direction of force direction with different cross section size.Such as, thin slice with small cross sections size can be folded between two adjacent thin slices with larger cross-section size, can form air gap 15 thus.
It should be understood that and be applicable to various types of compressor or other vibrative equipment according to vibration isolator of the present utility model; The quantity, size, structure etc. of vibration isolator can change according to embody rule situation; And compressor can be connected with vibration isolator directly or indirectly by the structure except leg.
Figure 13 is the schematic diagram changed along with operating mode according to axial displacement and the rigidity of vibration isolator of the present utility model.As shown in figure 13, under steady state operating conditions (being left side shown in figure), namely, when mainly there is the vibration of compressor self generation, the axial displacement of vibration isolator 10 is less, and air gap 15 is not closed, now, the effective cross-sectional area A of vibration isolator 10 is less, and therefore the rigidity of vibration isolator 10 is less, effectively can lower the vibration that when being run by compressor 20, self produces.Under external impact operating mode (being right side shown in figure), the axial displacement of vibration isolator 10 is larger, air gap 15 is closed, now, the effective cross-sectional area A ' of vibration isolator 10 is larger than aforementioned effective cross-sectional area A, therefore the rigidity of vibration isolator 10 becomes large, can the displacement of limit compression machine 20 effectively.
Although described various mode of execution of the present utility model in detail at this, but should be appreciated that the utility model is not limited to the embodiment described in detail and illustrate here, other modification and variant can be realized when not departing from essence of the present utility model and scope by those skilled in the art.All these modification and variant all fall in scope of the present utility model.And all components described here can be replaced by component equivalent in other technologies.
Claims (19)
1. a vibration isolator (10), described vibration isolator (10) in axial direction has first surface (14) and the second surface (12) relative with described first surface (14), and described vibration isolator (10) comprising:
The entity portion (110) of described second surface (12) is extended to along described axial direction from described first surface (14), and
Contiguous described entity portion (110) and extend to the air gap portion (150) of described second surface (12) along described axial direction from described first surface (14), at least one air gap (15) is provided with in described air gap portion (150)
Wherein, described at least one air gap (15) is configured to: closedly under the first operating mode make described vibration isolator (10) have the first rigidity, and closedly at least in part under the second operating mode makes described vibration isolator (10) have second rigidity larger than described first rigidity.
2. vibration isolator (10) as claimed in claim 1, wherein, described air gap portion (150) is arranged on the outside of described entity portion (110) along the horizontal direction perpendicular to described axial direction, and described air gap (15) extends from the outer side surface (16) of described air gap portion (150) towards described entity portion (110).
3. vibration isolator (10) as claimed in claim 1, wherein, described air gap portion (150) is arranged on the inner side of described entity portion (110) along the horizontal direction perpendicular to described axial direction.
4. vibration isolator (10) as claimed in claim 3, wherein, described vibration isolator (10) also comprises the interstice portion (160) being arranged on described entity portion (110) outside along described horizontal direction, and described interstice portion (160) comprises at least one air gap (15).
5. vibration isolator (10) as claimed in claim 1, described vibration isolator (10) comprises multiple air gap portion (150) and multiple entity portion (110), and described multiple air gap portion (150) and described multiple entity portion (110) are alternately arranged around the central axis of described vibration isolator (10).
6. the vibration isolator (10) as described in claim 3 or 4, wherein, described vibration isolator (10) also comprises the vent (19) for being communicated with described air gap (15) and ambient atmosphere.
7. the vibration isolator (10) according to any one of claim 1 to 5, wherein, described vibration isolator (10) also comprise the centre being arranged on described vibration isolator (10) for through fastening piece to install the mounting hole (13) of described vibration isolator (10).
8. vibration isolator (10) as claimed in claim 7, wherein, described air gap (15) circumferentially direction continuously or intermittently extends, or on described axial direction, continuously or intermittently extends in a spiral form, or extends in the form of a step in described circumferential direction.
9. vibration isolator (10) as claimed in claim 7, wherein, described vibration isolator (10) comprises multiple air gap (15), and described multiple air gap (15) has identical size and structure.
10. vibration isolator (10) as claimed in claim 7, wherein, described vibration isolator (10) comprises multiple air gap (15), and described multiple air gap (15) is configured so that:
A) at least two air gaps in described multiple air gap (15) have the different degree of depth in a lateral direction perpendicular to described axial direction; And/or
B) at least two air gaps in described multiple air gap (15) have different height on described axial direction.
11. vibration isolators (10) as claimed in claim 7, wherein, the height on the described axial direction of described air gap (15) is in the scope of 0.5mm to 3mm.
12. vibration isolators (10) as claimed in claim 7, wherein, described vibration isolator (10) comprises multiple air gap (15), described multiple air gap (15) described axial direction, circumferential direction and perpendicular at least one direction in the horizontal direction of described axial direction alignedly arrange, abreast arrange or arrange alternately.
13. vibration isolators (10) as claimed in claim 7, wherein, described vibration isolator (10) is in cylindric, and/or described vibration isolator (10) is made up of rubber material.
14. vibration isolators (10) as claimed in claim 7, wherein, described vibration isolator (10) forms, or is formed by the thin slice of superposition different size.
15. 1 kinds of compressor assemblies, described compressor assembly comprises compressor (20) and the vibration isolator according to any one of claim 1 to 14 (10), wherein, the supporting leg (22) of described compressor (20) is mounted on the support structure via described vibration isolator (10).
16. compressor assemblies as claimed in claim 15, wherein, are respectively provided to a few vibration isolator (10) in the upper side and lower side of described supporting leg (22).
17. compressor assemblies as claimed in claim 16, wherein, the described vibration isolator (10) of the described upside and described downside that are positioned at described supporting leg (22) has different structure and/or different size.
18. compressor assemblies as claimed in claim 15, wherein, via the fastening piece (30) inserted in the mounting hole of described vibration isolator (10) and sleeve (40), described supporting leg (22) is mounted to described supporting structure, wherein, described sleeve (40) to be arranged between described fastening piece (30) and described vibration isolator (10) and to be configured to can control when described supporting leg (22) is mounted to described supporting structure the preload of described vibration isolator (10).
19. compressor assemblies as described in any one in claim 15 to 18, wherein, described compressor assembly is the air-conditioning system for the traffic tool, and/or described compressor (20) is horizontal compressor.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520135415.XU CN204512264U (en) | 2015-03-10 | 2015-03-10 | Vibration isolator and compressor system comprising same |
| PCT/CN2016/075987 WO2016141878A1 (en) | 2015-03-10 | 2016-03-09 | Vibration isolator and compressor system comprising same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520135415.XU CN204512264U (en) | 2015-03-10 | 2015-03-10 | Vibration isolator and compressor system comprising same |
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| Publication Number | Publication Date |
|---|---|
| CN204512264U true CN204512264U (en) | 2015-07-29 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520135415.XU Active CN204512264U (en) | 2015-03-10 | 2015-03-10 | Vibration isolator and compressor system comprising same |
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| Country | Link |
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| CN (1) | CN204512264U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016141878A1 (en) * | 2015-03-10 | 2016-09-15 | 艾默生环境优化技术(苏州)有限公司 | Vibration isolator and compressor system comprising same |
| CN106032829A (en) * | 2015-03-10 | 2016-10-19 | 艾默生环境优化技术(苏州)有限公司 | Vibration isolator and compressor system comprising same |
-
2015
- 2015-03-10 CN CN201520135415.XU patent/CN204512264U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016141878A1 (en) * | 2015-03-10 | 2016-09-15 | 艾默生环境优化技术(苏州)有限公司 | Vibration isolator and compressor system comprising same |
| CN106032829A (en) * | 2015-03-10 | 2016-10-19 | 艾默生环境优化技术(苏州)有限公司 | Vibration isolator and compressor system comprising same |
| CN106032829B (en) * | 2015-03-10 | 2021-05-11 | 艾默生环境优化技术(苏州)有限公司 | Vibration isolator and compressor system comprising same |
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