CN204083032U - A kind of hydraulic mount - Google Patents
A kind of hydraulic mount Download PDFInfo
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- CN204083032U CN204083032U CN201420519083.0U CN201420519083U CN204083032U CN 204083032 U CN204083032 U CN 204083032U CN 201420519083 U CN201420519083 U CN 201420519083U CN 204083032 U CN204083032 U CN 204083032U
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- diaphragm
- runner
- high frequency
- flange
- circle
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Abstract
The utility model provides a kind of hydraulic mount and has external casing, main damping body, spacer body and sealed bottom body, it is overall low frequency runner and high frequency diaphragm that spacer body comprises sulfuration, low frequency runner is provided with flow-disturbing flange, high frequency diaphragm is provided with otch.The low frequency runner of overall sulfuration and high frequency diaphragm add the stability of suspension work, flow-disturbing flange replaces flow-disturbing dish to reduce because flow-disturbing valve snail bolt loosens or the come off abnormal sound or interference that cause under vibration, high pressure diaphragm is arranged otch reduce high frequency under dynamic stiffness, form earial drainage effect when hydraulic mount is subject to larger pressure, prevent the entirety of high frequency diaphragm from breaking.
Description
Technical field
The utility model relates to car engine suspension technical field, particularly relates to a kind of hydraulic mount.
Background technique
For engine side suspension, in order to improve its anti-vibration performance in high frequency, be generally all designed to hydraulic mount, its Specifeca tion speeification of hydraulic mount to have under the output ratio of Q-switching to free running and high frequency dynamic stiffness etc.
Static stiffness refers to the deformation quantity that object produces under certain External Force Acting; Dynamic stiffness is the definition relative to Static stiffness, and dynamic stiffness is then the deformation quantity that object produces under the External Force Acting under certain frequency; The output ratio of Q-switching to free running is the ratio of dynamic stiffness and Static stiffness.
As shown in Figure 1, Figure 2, Figure 3 shows, be the hydraulic suspension structure schematic diagram of prior art one.
Hydraulic mount comprises perimeter defense housing 1, rubber spring 2, flow-disturbing dish 3, runner platen 41, decoupling zero diaphragm 42, runner 43 and rubber counterdie 5.
Wherein, decoupling zero diaphragm 42 is fitted in runner 43 neutral position and forms partitioned portion 4 by runner platen 41.Hydraulic mount inside is divided into upper liquid chamber 6 and lower liquid chamber 7 by partitioned portion 4, when low frequency large amplitude, liquid directly circulates between upper liquid chamber 6 and lower liquid chamber 7 via runner 43, and the fluid resistance now produced through small channel by liquid stream is comparatively large, is the main contributions element producing low frequency damping.Under engine idle and high-speed working condition, because amplitude is less, frequency is very fast, liquid almost effectively cannot flow in runner 43, only has the volume-variation realizing between upper liquid chamber 6 and lower liquid chamber 7 by the distortion of decoupling zero diaphragm 42, therefore the rigidity of decoupling zero diaphragm 42 has just become impact now to suspend the key factor of dynamic stiffness, and the thickness of decoupling zero diaphragm 42, size and structure and rubber material are the principal element places affecting its performance.Decoupling zero diaphragm 42 is sulfided by diaphragm main body 421 (diaphragm main body is quality of rubber materials) and diaphragm skeleton 422 (diaphragm skeleton is metal material) and is formed in the prior art.While there is deformation in decoupling zero diaphragm 42, the distortion of the main spring rubber 2 of flow-disturbing dish 3 and its periphery creates the change of volume, also the liquid upwards sprung up is there is in liquid in the defluent situation of entirety, and on flow-disturbing dish, in the semi-enclosed little liquid chamber 61 of 3 side, form the flowing of local, the now this disturbance of flow-disturbing dish 3 exacerbates the fluid turbulence of upper liquid chamber 6, add the loss of energy, reduce the dynamic rate under high frequency.
As can be seen here, what affect the output ratio of Q-switching to free running is decoupling zero mambrane tension, and what affect dynamic stiffness under high frequency is flow-disturbing dish.Therefore, select Low rigidity decoupling zero diaphragm to be conducive to obtaining the less output ratio of Q-switching to free running, be beneficial to isolation high frequency small amplitude motion, but its drag angle diminishes, be unfavorable for isolation low frequency large-amplitude vibration.In addition, because suspension is by the restriction in engine compartment space, small volume, for hydraulic mount, its inner space is just limited especially, and the existence of flow-disturbing dish can cause following three problems in this case:
(1) make inner space arrange to be restricted, also making rubber spring need consideration to evade flow-disturbing dish when designing, the performances such as durability needing sometimes make sacrifices;
(2) there is risk in reliability, easily occurs coming off, producing the problems such as abnormal sound because of movement interference;
(3) cost is higher, comprises the assembly cost of the cost of processed materials purchased, die cost and production line.
As shown in Figure 4, be the hydraulic suspension structure schematic diagram of prior art two.
Setting in view of above-mentioned flow-disturbing dish causes three problems, eliminates flow-disturbing dish in prior art two, but can increase high frequency dynamic stiffness accordingly when cancelling flow-disturbing dish.Therefore a less top liquid chamber 62 is provided with on upper liquid chamber top as buffer area.Although but this kind of scheme to a certain degree reduce high frequency dynamic stiffness, do not reach the effect being provided with flow-disturbing dish.
Model utility content
Embodiment of the present utility model provides a kind of hydraulic mount, dynamic stiffness when flow-disturbing dish reduces dither is replaced by arranging annular boss in high frequency diaphragm periphery, by the integrated vulcanizing of high frequency diaphragm and low frequency runner, and be provided with otch on high frequency diaphragm, reduce the output ratio of Q-switching to free running.
For achieving the above object, the utility model embodiment provides following technological scheme:
A kind of hydraulic mount has external casing, main damping body, spacer body and sealed bottom body.
External casing comprises upper shell and lower shell body, and main damping body comprises main damping pad and main damping pad fixed plate, and spacer body comprises low frequency runner and high frequency diaphragm, and sealed bottom body comprises bottom film sheet and assembling pressure ring.
Low frequency runner entirety is in circular, the groove that its outer toroid sidewall is provided with to direction, the center of circle forms the export-oriented opening of runner, the flange-shape that its inner circle ring-side wall is provided with to direction, the center of circle becomes diaphragm reinforcing part, in its upper surface, annulus place is provided with flow-disturbing flange, and its lower surface outer shroud place is provided with sealed groove.High frequency diaphragm is arranged on low frequency runner inner circle ring place, and its periphery and diaphragm reinforcing part integrated vulcanizing, high frequency diaphragm neutral position is provided with otch.
As preferably, upper shell is provided with upper shell crimp, lower shell body is provided with lower shell body crimp, upper shell crimp and lower shell body crimp are all arranged at the link position of upper shell and lower shell body, the width of lower shell body crimp is greater than the width of upper shell crimp, and lower shell body crimp is upwards bent to form edge structure.
Main damping pad top has supporting portion, and bottom has vibration damping portion.
In supporting portion, sulfuration has metal-cored, with the sulfuration of main damping pad fixed plate bottom vibration damping portion.
Metal-cored along Y extension limited location flange, the supporting portion of its outside sulfuration is provided with vibration damping flange along the two ends of automobile running axis, and the height of vibration damping flange successively decreases along the both sides of vehicle traveling direction axis.
Damping pad fixed plate and sulfuration position, vibration damping portion stretch out and are bent with holding flange, and bent inwards bottom it sealing flange.
Bottom film sheet edge is provided with seal boss.
As preferably, flow-disturbing flange wedgewise, its center of circle outer side surface round relative to low frequency runner place is perpendicular to low frequency runner upper surface, its center of circle inner side surface round relative to low frequency runner place extends downward the upper surface of diaphragm reinforcing part, and inner side surface becomes 95 ° of-100 ° of angles with the upper surface of diaphragm reinforcing part.
As preferably, flow-disturbing flange top is 5-6mm to the height of low frequency runner upper surface, and flow-disturbing flange top is 9-10mm to the height of diaphragm reinforcing part upper surface, and flow-disturbing flange top width is 1.5-3mm.
As preferably, high frequency diaphragm is formed from diaphragm reinforcing part sulfuration position to direction, the high frequency diaphragm center of circle and strengthens extension part and diaphragm vibration portion.
The thickness in diaphragm vibration portion is less than the thickness strengthening extension part, and diaphragm vibration portion is not more than 2 millimeters with the thickness difference strengthening extension part.
As preferably, otch is cross shape, and the cross searching of otch is the center of circle of high frequency diaphragm.
As preferably, the ratio of the radius of a circle at otch place and high frequency diaphragm place radius of a circle between diaphragm reinforcing part is between 0.5-0.6.
The beneficial effect that technical solutions of the utility model are brought is:
Cancel flow-disturbing dish, low frequency runner is provided with annular boss, provides the design space of main damping pad, reduce because flow-disturbing valve snail bolt loosens or the come off abnormal sound or interference that cause under vibration.Low frequency runner and the overall sulfuration of high frequency diaphragm, add the stability of suspension work.High pressure diaphragm is arranged otch reduce high frequency under dynamic rate, form earial drainage effect when hydraulic mount is subject to larger pressure, prevent the entirety of high frequency diaphragm from breaking, cause the disappearance of the low dynamic stiffness characteristic of the large damping characteristic of the low frequency of hydraulic mount, high frequency.
Accompanying drawing explanation
Fig. 1 is the hydraulic suspension structure schematic diagram of prior art one;
Fig. 2 is the hydraulic suspension partitioned portion structural representation of prior art one;
Fig. 3 is the hydraulic mount decoupling zero diaphragm structure schematic diagram of prior art one;
Fig. 4 is the hydraulic suspension structure schematic diagram of prior art two;
Fig. 5 is hydraulic suspension structure schematic diagram of the present utility model;
Fig. 6 is hydraulic mount upper shell internal structure schematic diagram of the present utility model
Fig. 7 is hydraulic mount sectional view partial enlarged drawing of the present utility model;
Fig. 8 is hydraulic suspension partitioned portion structural representation of the present utility model.
Symbol description:
1 protective casing 113 vibration damping flange
The main damping pad fixed plate of 2 rubber spring 12
3 flow-disturbing dish 121 holding flanges
4 partitioned portion 122 sealing flanges
41 runner platen 13 upper shells
42 decoupling zero diaphragm 131 upper shell crimps
421 diaphragm main body 14 lower shell bodys
422 diaphragm skeleton 141 lower shell body crimps
43 runner 141 outer casing stands
5 rubber counterdie 15 low frequency runners
The export-oriented opening of 6 upper liquid chamber 151 runners
61 little liquid chamber 152 diaphragm reinforcing parts
62 top liquid chamber 153 flow-disturbing flanges
7 times liquid chamber 154 sealed grooves
8 kingbolt 16 high frequency diaphragms
9 insulating cell 161 otch
10 metal-cored 162 strengthen extension part
101 defining flange 163 diaphragm vibration portions
11 main damping pad 17 bottom film sheet
111 vibration damping portion 171 seal bosses
Pressure ring is assembled in 112 supporting portions 18
Embodiment
For enabling above-mentioned purpose of the present utility model, feature and advantage become apparent more, are described in detail embodiment of the present utility model below in conjunction with accompanying drawing.
Set forth a lot of detail in the following description so that fully understand the utility model, but the utility model can also adopt other to be different from alternate manner described here to implement, those skilled in the art can when doing similar popularization without prejudice to when the utility model intension, and therefore the utility model is by the restriction of following public specific embodiment.
Shown in figure 5 to Fig. 8, a kind of hydraulic mount has external casing, main damping body, spacer body and sealed bottom body.
External casing comprises upper shell 13 and lower shell body 14.
Upper shell 13 and lower shell body 14 are sealed by bound edge, the upper shell crimp 131 to hull outside bending is formed in the present embodiment bottom upper shell 13, upper shell crimp 141 to hull outside bending is formed on lower shell body top, the width of lower shell body crimp 141 is greater than the width of upper shell crimp 131, and is upwards bent to form bound edge sealing configuration.
Also outer casing stand is fixedly welded with, for being fixedly connected with vehicle body outside lower shell body 141.
Main damping body comprises main damping pad 11 and main damping pad fixed plate 12.
Main damping pad 11 is divided into upper and lower two-part, its top be there is the supporting portion 111 of supporting effect, bottom is the vibration damping portion 112 with damping effect.The inner sulfuration in supporting portion 111 has metal-cored 10, and metal-cored 10 inside are fixed with the kingbolt 8 for connecting power assembly.Metal-cored 10 are outward extended with defining flange 101 along the longitudinal axis (kingbolt 8 place axle), at defining flange 101, the two ends of vehicle traveling direction (vehicle traveling direction is arrow points direction in Fig. 6) axis are provided with vibration damping flange 113, this vibration damping flange 113 is flexuose, and the height that vibration damping flange 113 protrudes successively decreases along the both sides of vehicle traveling direction axis.Defining flange 101 upper surface engages with upper shell 13 top inner surface and compresses.When automobile running accelerate suddenly and retarding braking, power assembly can be subject to two end motions of effect along direction of travel of inertia, drive the kingbolt 8 be fixedly connected on metal-cored 10, therefore defining flange 101 also can move thereupon, in violent acceleration and deceleration situation, defining flange can with upper shell 13 contact internal walls, cause dynamic stiffness to be interfered, cause upper shell 13 distortion so that damage.Therefore cushion by arranging vibration damping flange 113 at surface of contact, but if disposable buffering is carried out to this kind of shock, the effect played is also not obvious, the damping block that vibration damping flange 113 protrudes successively decreases successively in vehicle traveling direction axis (namely first contact position) both sides, and its vibration reduction and cushioning segmentation in making contact process is realized.
Upper shell 13 top is also provided with insulating cell 9, this insulating cell 9 is nonrigid material, do something in disregard of obstacles and relate to for preventing the metallic member of hydraulic mount upper shell 13 and mounting bracket (not shown on the figure) formative dynamics be arranged on kingbolt 8, and play insulating effect.
Vibration damping portion 112 is rubber or the elastic material with close elasticity indexes, and with the sulfuration of main shock mounting plate 12 bottom it, the equal sulfuration of main shock mounting plate outer surface has rubber.Bottom main shock mounting plate 12 and vibration damping portion 112, sulfuration position stretches out and is bent with holding flange 121, and bent inwards bottom it sealing flange 122.
Holding flange 121 is arranged on the compression position of upper shell crimp 131 and lower shell body crimp 141, for fixing main damping body.
Due to road bump or other factors in vehicle traveling process, power assembly can apply pressure to suspension by the vertical direction, and this pressure is mainly from suspension top, and suspension realizes mainly through vibration damping portion 112 this kind of pressure buffer.Main shock mounting plate 12 bottom vibration damping portion 112 just carries the major component of pressure, finally act on the lower shell body crimp 141 of lower shell body 14, therefore upper shell 13 is that lower shell body crimp 141 upwards superscribes housing crimp 131 with the bound edge of lower shell body 14 attachment portion in the present embodiment, and lower shell body crimp 141 ensure that its rigid by repeatedly bending.
If the mode of the lower crimp of crimp parcel, because pressure acts predominantly on lower shell body, may cause distortion or the damage of lower shell body in employing in the situation applying larger pressure.
Spacer body comprises low frequency runner 15 and high frequency diaphragm 16.
Hydraulic mount inside is divided into top liquid chamber and bottom liquid chamber by spacer body.
Low frequency runner 15 entirety is in circular, the groove that its outer toroid sidewall is provided with to direction, the center of circle forms the export-oriented opening 151 of runner, the export-oriented opening 151 of runner compresses with main vibration damping point fixed plate 12 madial wall the flow channel for liquids forming low frequency runner 15, is provided in the flow of fluid of hydraulic mount inside during engine tumble.
The flange-shape that low frequency runner 15 inner circle ring-side wall is provided with to direction, the center of circle becomes diaphragm reinforcing part 152, and in its upper surface, annulus place is provided with flow-disturbing flange 153, and its lower surface outer shroud place is provided with sealed groove 154.
Flow-disturbing flange 153 is wedgewise substantially, the center of circle outer side surface that it is relative and low frequency runner 15 place is round is perpendicular to low frequency runner 15 upper surface, its center of circle inner side surface that is relative and low frequency runner 15 place circle extends downward the upper surface of institute's sheet reinforcing part 152, and inner side surface becomes 95 ° of-100 ° of angles with the upper surface of diaphragm reinforcing part 152.
The runner top liquid chamber through hole (not shown on figure) of the contiguous low frequency runner 15 of flow-disturbing flange 153 outer side surface, when engine tumble, needs to ensure the smooth and easy of the fluid exchange between hydraulic mount top liquid chamber and bottom liquid chamber.Flow-disturbing flange 153 mainly plays turbulent effect and should not affect the flowing of low frequency runner 15 runner internal liquid, if flow-disturbing flange 153 outer side surface tilts laterally, obstruction can be caused to runner top liquid chamber through hole (not shown on figure), affect the fluid exchange between top liquid chamber and bottom liquid chamber.If flow-disturbing flange 153 outer side surface tilts to the inside, then can form horn mouth shape (inversion wedge shape) in runner top liquid chamber through hole (not shown on figure) top, the instantaneous difference of top liquid chamber and the bottom liquid chamber upper and lower flow velocity of liquid when fluid exchange can be caused, be unfavorable for the vibration damping and energy-absorbing effect that hydraulic mount vibrates power assembly.And flow-disturbing flange 153 outer side surface perpendicular to low frequency runner 15 upper surface time, top liquid chamber and bottom liquid chamber carry out the unimpeded and flow velocity of fluid exchange without instantaneous difference.
The height of flow-disturbing flange 153 also affects the flow of fluid of hydraulic mount low-frequency vibration while playing liquid action of turbulent flow, if flow-disturbing flange 153 top, to the excessive height of low frequency runner 15 upper surface, hinders the flowing of liquid, if highly too low, turbulent DeGrain, therefore, in comparatively preferred embodiment, flow-disturbing flange 153 top is 5-6mm to the height of low frequency runner 15 upper surface.
High frequency diaphragm 16 is arranged on annulus place in low frequency runner 15, its periphery and diaphragm reinforcing part 152 integrated vulcanizing.Diaphragm reinforcing part 152 sulfuration position is formed to direction, high frequency diaphragm 16 center of circle and strengthens extension part 162 and diaphragm vibration portion 163.High frequency diaphragm 16 neutral position is provided with otch 161.
Under engine idle and high-speed working condition, high frequency diaphragm 16 realizes the volume-variation of top liquid chamber and bottom liquid chamber by deformation.The deformation that this kind of vibration brings is more violent on microcosmic, and in the present embodiment, high frequency diaphragm 16 and low frequency runner 15 integrated vulcanizing are formed, its diaphragm reinforcing part 152 and the sulfuration position of high frequency diaphragm 16 have thickness less be connected part.When dither, if this position produces vibration generation, deformation ratio is easier to breakage, and high frequency diaphragm 16 can be caused cannot to continue to use.Therefore strengthen being easier to damage location by arranging reinforcement extension part 162, and high frequency diaphragm 16 is divided into reinforcement extension part 162 and 163 two, diaphragm vibration portion part.Change the dither position of high frequency diaphragm 16, high frequency diaphragm 16 is effectively protected.Therefore, in comparatively preferred embodiment, diaphragm vibration portion 163 thickness is less than described reinforcement extension part 162, vibration during high frequency is mainly acted in diaphragm vibration portion 163, and thickness difference is not more than 2 millimeters.
In order to obtain the lower output ratio of Q-switching to free running, needing the Static stiffness reducing diaphragm vibration portion 163, in above-mentioned technological scheme, is be divided into by high frequency diaphragm 16 strengthening extension part 162 and 163 two, diaphragm vibration portion part.Although effectively Static stiffness can be lowered by reducing the thickness in diaphragm vibration portion 163, in vehicle traveling process, when run into significantly jolt or similar, power assembly can apply larger pressure to hydraulic mount instantaneously.Liquid now in hydraulic mount does not carry out fluid exchange by the runner in low-frequency flow road 15, but pressure is applied to high frequency diaphragm 16, high frequency diaphragm 16 bear larger pressure produce deformation time easily damaged, therefore in the technical solution of the utility model, high frequency diaphragm 16 neutral position is provided with otch 161.
The effect of otch 161 is when high frequency diaphragm 16 is when bearing larger pressure instantaneously, the fluid exchange that liquid can be undertaken between top liquid chamber and bottom liquid chamber by otch, makes high frequency diaphragm 16 not fragile when bearing larger pressure instantaneously.But high frequency diaphragm 16 still needs to have certain Static stiffness, in embodiment of the present utility model, as a kind of preferred embodiment, otch 161 is cross shape, and the cross searching of otch 161 is the center of circle of high frequency diaphragm 16, from otch 161 center to the end-to-end distance of cross from equal.The radius of a circle at otch 161 place and the ratio of high frequency diaphragm 16 place radius of a circle between diaphragm reinforcing part 152 are between 0.5-0.6.Both having ensure that the Static stiffness of high frequency diaphragm 16, and also having made high frequency diaphragm 16 unsuitable damaged when bearing larger pressure instantaneously.
Sealed bottom body comprises bottom film sheet 17 and assembling pressure ring 18.
Bottom film sheet 17 is elastic material, is arranged on bottom low frequency runner 15, and the upper surface of its peripheral edge is provided with the seal boss 171 matched with sealed groove 154.Assembling pressure ring 18 coordinates with sealing flange 122, seals bottom film sheet 17 and low frequency runner 15.Holding space between bottom film sheet 17 and spacer body forms bottom liquid chamber.
Bottom film sheet 17 is sealed to bottom main shock mounting plate 12 by assembling pressure ring 18, seals fixing as a whole, ensure that the sealing of hydraulic mount internal liquid with main damping body.
Although the utility model is described in conjunction with above embodiment, but the utility model is not defined to above-described embodiment, and only by the restriction of claims, those of ordinary skill in the art can easily modify to it and change, but do not leave essential idea of the present utility model and scope.
Claims (9)
1. a hydraulic mount has external casing, main damping body, spacer body and sealed bottom body;
Described external casing comprises upper shell (13) and lower shell body (14);
Described main damping body comprises main damping pad (11) and main damping pad fixed plate (12);
Described spacer body comprises low frequency runner (15) and high frequency diaphragm (16);
Described sealed bottom body comprises bottom film sheet (17) and assembling pressure ring (18);
It is characterized in that: described low frequency runner (15) is in circular, the groove that its outer toroid sidewall is provided with to direction, the center of circle forms the export-oriented opening (151) of runner, the flange-shape that its inner circle ring-side wall is provided with to direction, the center of circle becomes diaphragm reinforcing part (152), in its upper surface, annulus place is provided with flow-disturbing flange (153), and its lower surface outer shroud place is provided with sealed groove (154); Described high frequency diaphragm (16) is arranged on the described interior annulus place of low frequency runner (15), its periphery and described diaphragm reinforcing part (152) integrated vulcanizing, described high frequency diaphragm (16) neutral position is provided with otch (161).
2. hydraulic mount according to claim 1, it is characterized in that: described upper shell (13) is provided with upper shell crimp (131), described lower shell body is provided with lower shell body crimp (141), described upper shell crimp (131) and described lower shell body crimp (141) are all arranged at the link position of described upper shell and described lower shell body (14), the width of described lower shell body crimp (141) is greater than the width of described upper shell crimp (131), and lower shell body crimp (141) is upwards bent to form edge structure.
3. hydraulic mount according to claim 1, is characterized in that: described main damping pad (11) top has supporting portion (111), and bottom has vibration damping portion (112);
Described supporting portion (111) interior sulfuration has metal-cored (10), described vibration damping portion (112) bottom and the sulfuration of described main damping pad fixed plate (12);
Described metal-cored (10) are along Y extension limited location flange (101), the described supporting portion (111) of its outside sulfuration is provided with vibration damping flange (113) along the two ends of automobile running axis, and the height of vibration damping flange (113) successively decreases along the both sides of vehicle traveling direction axis;
Described damping pad fixed plate (12) and described vibration damping portion (112) sulfuration position stretch out and are bent with holding flange (121), and bent inwards bottom it sealing flange (122).
4. hydraulic mount according to claim 1, is characterized in that: described bottom film sheet (17) edge is provided with seal boss (171).
5. hydraulic mount according to claim 1, it is characterized in that: described flow-disturbing flange (153) wedgewise, its center of circle outer side surface relative to described low frequency runner (15) place circle is perpendicular to described low frequency runner (15) upper surface, it extends downward the upper surface of described diaphragm reinforcing part (152) relative to the center of circle inner side surface of described low frequency runner (15) place circle, and described inner side surface becomes 95 ° of-100 ° of angles with the upper surface of described diaphragm reinforcing part (152).
6. hydraulic mount according to claim 1, it is characterized in that: described flow-disturbing flange (153) top is 5-6mm to the height of described low frequency runner (15) upper surface, described flow-disturbing flange (153) top is 9-10mm to the height of described diaphragm reinforcing part (152) upper surface, and described flow-disturbing flange (153) top width is 1.5-3mm.
7. hydraulic mount according to claim 1, is characterized in that: described high frequency diaphragm (16) is formed from described diaphragm reinforcing part (152) sulfuration position to described high frequency diaphragm (16) direction, the center of circle strengthens extension part (162) and diaphragm vibration portion (163);
The thickness of described diaphragm vibration portion (163) is less than the thickness of described reinforcement extension part (162), and described diaphragm vibration portion (163) is not more than 2 millimeters with the thickness difference of described reinforcement extension part (162).
8. hydraulic mount according to claim 1, is characterized in that: described otch (161) is cross shape, and the cross searching of described otch (161) is the center of circle of described high frequency diaphragm (16).
9. hydraulic mount according to claim 1, is characterized in that: the ratio of the radius of a circle at described otch (161) place and described high frequency diaphragm (16) place radius of a circle between described diaphragm reinforcing part (152) is between 0.5-0.6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420519083.0U CN204083032U (en) | 2014-09-10 | 2014-09-10 | A kind of hydraulic mount |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420519083.0U CN204083032U (en) | 2014-09-10 | 2014-09-10 | A kind of hydraulic mount |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204083032U true CN204083032U (en) | 2015-01-07 |
Family
ID=52175755
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420519083.0U Withdrawn - After Issue CN204083032U (en) | 2014-09-10 | 2014-09-10 | A kind of hydraulic mount |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204083032U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104235254A (en) * | 2014-09-10 | 2014-12-24 | 安徽江淮汽车股份有限公司 | Hydraulic mount |
-
2014
- 2014-09-10 CN CN201420519083.0U patent/CN204083032U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104235254A (en) * | 2014-09-10 | 2014-12-24 | 安徽江淮汽车股份有限公司 | Hydraulic mount |
| CN104235254B (en) * | 2014-09-10 | 2016-02-03 | 安徽江淮汽车股份有限公司 | A kind of hydraulic mount |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20150107 Effective date of abandoning: 20160203 |
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| C25 | Abandonment of patent right or utility model to avoid double patenting |