CN111577811A - Viscous damper - Google Patents
Viscous damper Download PDFInfo
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- CN111577811A CN111577811A CN202010468069.2A CN202010468069A CN111577811A CN 111577811 A CN111577811 A CN 111577811A CN 202010468069 A CN202010468069 A CN 202010468069A CN 111577811 A CN111577811 A CN 111577811A
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- Prior art keywords
- inner sleeve
- outer sleeve
- piston
- sleeve
- viscous damper
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- 238000006073 displacement reaction Methods 0.000 claims abstract description 22
- 238000007789 sealing Methods 0.000 claims abstract description 17
- 230000002159 abnormal effect Effects 0.000 claims abstract description 12
- 238000013016 damping Methods 0.000 claims description 22
- 230000003068 static effect Effects 0.000 claims description 5
- 230000000694 effects Effects 0.000 abstract description 8
- 230000035939 shock Effects 0.000 abstract description 6
- 230000004044 response Effects 0.000 abstract description 3
- 238000005299 abrasion Methods 0.000 abstract description 2
- 230000008859 change Effects 0.000 description 10
- 239000007788 liquid Substances 0.000 description 10
- 230000009471 action Effects 0.000 description 7
- 238000010521 absorption reaction Methods 0.000 description 3
- 230000008602 contraction Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000021715 photosynthesis, light harvesting Effects 0.000 description 2
- 230000003111 delayed effect Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
Images
Classifications
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- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/30—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium with solid or semi-solid material, e.g. pasty masses, as damping medium
- F16F9/303—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium with solid or semi-solid material, e.g. pasty masses, as damping medium the damper being of the telescopic type
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- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
-
- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3214—Constructional features of pistons
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- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3235—Constructional features of cylinders
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- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/3405—Throttling passages in or on piston body, e.g. slots
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- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/362—Combination of sealing and guide arrangements for piston rods
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- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/368—Sealings in pistons
-
- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/504—Inertia, i.e. acceleration,-sensitive means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
The invention discloses a viscous damper, which comprises a cylinder barrel, a piston assembly, a hollow inner sleeve and a hollow outer sleeve, wherein the cylinder barrel is provided with a piston rod; the left end of the inner sleeve is fixedly connected with the right end of the cylinder barrel, the inner sleeve is sleeved in the hollow cavity of the outer sleeve, and the inner sleeve and the outer sleeve can move relatively; a locking device which can stop the relative movement of the inner sleeve and the outer sleeve is arranged between the inner sleeve and the outer sleeve; the locking device enables the relative movement distance S1 of the inner sleeve and the outer sleeve to be not less than the displacement S2 of the piston forced by daily load, and S1 is not more than the displacement S3 of the piston forced by abnormal load. According to the invention, the piston rod does not displace in daily load, and a sealing element in contact with the piston rod is protected from abrasion. Under the abnormal load, because there is not the clearance, it is more sensitive to vibrations response, and the power consumption efficiency is higher, and the shock attenuation effect is better.
Description
Technical Field
The invention belongs to the field of engineering shock absorption, and particularly relates to a viscous damper.
Background
The viscous damper is an energy dissipation and shock absorption device, is introduced to the field of engineering structures from the initial aerospace field, is developed for decades, has mature theoretical research, has the advantages of high energy dissipation efficiency, large stroke and the like, and obtains a very good shock absorption effect in engineering practice, so that the viscous damper is widely applied to various structural engineering. Especially to the shock attenuation of large-span bridge, because other damping device can't provide enough big stroke to satisfy large-scale deformation of large-span bridge under operating mode such as earthquake, the viscous damper is undoubtedly the most effective damping device.
The viscous damper is a speed-related damping device, the magnitude of the output damping force is determined by the speed of the movement speed, and the higher the movement speed is, the larger the damping force is. Under the daily load action of driving brake, temperature change and the like, the motion speed of the piston of the viscous damper relative to the cylinder barrel is very slow, the damping force is hardly output, the free deformation of the structure is not hindered, and the characteristic is very favorable for the stress of the structure.
However, even under a small daily load such as a traveling brake or a temperature change, a small displacement change of the piston rod (for example, a small displacement of the piston rod due to expansion and contraction with heat) occurs in the viscous damper. In the reciprocating motion of day to day, the seal of the viscous damper is constantly subjected to the friction of the piston rod, and the accumulated friction distance is very large in a service period of several decades. The loss of the sealing element gradually occurs in friction, the sealing performance is continuously reduced, and the hidden danger of large oil leakage exists. Once leakage occurs, the damping effect of the viscous damper is greatly reduced or even completely disabled, and the vibration energy cannot be absorbed and consumed when an earthquake comes, so that effective protection cannot be provided for the structure.
Therefore, patent 201821563946.9 discloses a liquid viscous damper with a free micro-motion device, which includes a liquid viscous damping device and a free micro-motion device for transmitting displacement and/or force to the liquid viscous damping device, wherein the free micro-motion device has an adjustable deformation in the damping direction of the liquid viscous damping device, the deformation is Smin-Smax, the free micro-motion device is in the damping direction of the liquid viscous damping device, the relative displacement of the structure connected with the liquid viscous damper is s, and when s is greater than Smax or is smaller than Smin, the free micro-motion device transmits the displacement which is not offset by the deformation to the liquid viscous damping device. This scheme has produced certain effect, for example can avoid brake and driving load to produce the disturbance to the viscous damper of liquid, has reduced the accumulative stroke that the viscous damper of liquid produced, also can take into account the influence of temperature deformation to the attenuator durability, has reduced the wearing and tearing volume of attenuator sealing member, and is longe-lived than current ordinary viscous damper of liquid. But this solution also introduces new drawbacks: due to the fact that the adjustable deformation is additionally designed, when large displacement such as earthquake occurs and energy consumption needs to be immediately damped, the response of the damper is delayed because the piston needs to move the deformation displacement first, and the damping effect is reduced.
In addition, the specific terms mentioned in the present application are defined as follows:
daily load: in the daily use process of the viscous damper matched with the structural engineering, inevitable loads such as service brake, temperature change and the like can cause small displacement change of the viscous damper.
Abnormal load: compared with the daily load, namely the load except the daily load, which can cause the structural engineering to be damaged and further cause the viscous damper to generate larger displacement, such as earthquake load, strong wind load and the like.
Disclosure of Invention
In view of the above problems, the present invention is directed to a new structural design such that the seal in contact with the piston rod is not worn under daily load; under the action of large loads such as earthquake and the like, the damping force can be immediately responded to generate the damping force, and the earthquake energy is consumed.
The technical scheme for solving the problems is as follows: a viscous damper comprises a cylinder barrel and a piston assembly arranged in the cylinder barrel, wherein the piston assembly comprises a piston capable of sliding in the cylinder barrel and a piston rod penetrating out of the piston, the cylinder barrel is divided into closed chambers by the piston, damping holes capable of communicating the closed chambers are formed in the piston, and the viscous damper further comprises a hollow inner sleeve and a hollow outer sleeve; the left end of the inner sleeve is fixedly connected with the right end of the cylinder barrel, the inner sleeve is sleeved in the hollow cavity of the outer sleeve, and the inner sleeve and the outer sleeve can move relatively;
a locking device which can stop the relative movement of the inner sleeve and the outer sleeve is arranged between the inner sleeve and the outer sleeve;
the locking device enables the relative movement distance S1 of the inner sleeve and the outer sleeve to be not less than the displacement S2 of the piston forced by daily load, and S1 to be not more than the displacement S3 of the piston forced by abnormal load.
In the scheme, only the inner sleeve and the outer sleeve move relatively under the action of daily load such as temperature change. Under the action of abnormal loads such as earthquakes, the generated displacement S3 is large and far exceeds S2, and the locking device plays a role, so that the inner sleeve and the outer sleeve are integrated into a whole and do not generate relative movement any more. Under the drive of abnormal load, the piston rod drives the piston to reciprocate, damping force is generated, energy is consumed, and the normal function of the viscous damper is exerted.
In the prior art, the values of S2 and S3 can be accurately calculated according to the application scenario of the damper, and are easily achieved by those skilled in the art. For example, the displacement amount S2 of expansion with heat and contraction with cold can be calculated from the change in temperature; from the minimum earthquake generated load S3 is calculated. The size of S1 was designed according to S2 and S3.
Furthermore, the locking device comprises two clamping grooves which are arranged around the outer wall of the inner sleeve at intervals and an elastic stopping device which is arranged on the outer sleeve; in an initial state, the setting area of the elastic stopping device is positioned between the two clamping grooves; the distance between the two card slots is 2 times S1;
the elastic stopping device can be clamped into the clamping groove to force the inner sleeve and the outer sleeve to be relatively static.
Preferably, the elastic stopping device comprises a clamping ring groove arranged around the inner wall of the outer sleeve, a clamping ring arranged in the clamping ring groove and a spring, a through hole communicated with the clamping ring groove is formed in the outer wall of the outer sleeve, the spring is arranged in the through hole, and a plug is arranged at the through hole;
one end of the spring is abutted to the clamping ring, and the other end of the spring is abutted to the plug.
Preferably, a wear-resistant ring is arranged on the outer wall of the inner sleeve and positioned between the two clamping grooves in a surrounding mode.
Furthermore, in order to ensure that the snap ring can be quickly clamped into the snap groove when passing through the snap groove and is tightly attached to the snap groove, the wall of the snap groove is a slope, and the width of the bottom of the snap groove is smaller than that of the opening of the snap groove;
the lower end of the clamping ring is provided with a chamfer which has the same inclination with the clamping groove wall and can be matched with the clamping groove wall.
In order to make the structure compact, the right end of the piston rod can extend into the hollow cavity of the inner sleeve, and the axes of the cylinder barrel, the piston rod, the inner sleeve and the outer sleeve are on the same straight line.
Furthermore, end covers are arranged at two ends of the cylinder barrel, static sealing elements are arranged at the joints of the end covers and the cylinder barrel, and dynamic sealing elements are arranged in contact areas of two ends of the piston rod and the end covers.
Furthermore, a left ear ring is fixedly connected to the left end of the piston rod; the right end of the outer sleeve is plugged, and a right earring is fixedly connected to the plugged part.
The invention has the following remarkable effects:
1. the design of the inner sleeve, the outer sleeve and the locking device ensures that the relative movement of the inner sleeve and the outer sleeve adapts to the stress change of the structure in daily load, the piston rod does not generate displacement, the sealing element in contact with the piston rod is protected from abrasion, and the service life of the sealing element can be effectively prolonged.
2. Under unusual loads such as earthquake, under locking device's effect, inner skleeve and outer sleeve close as an organic whole immediately, no longer take place relative motion between the two, become a conventional viscous damper, piston rod and piston carry out reciprocating motion in the cylinder, because do not have the clearance, more sensitive to vibrations response, the power consumption efficiency is higher, and the shock attenuation effect is better.
Drawings
The invention will be further explained with reference to the drawings.
FIG. 1 is a schematic structural view of the viscous damper of the present invention under a normal loading condition.
Fig. 2 is a view a-a of fig. 1.
FIG. 3 is a schematic view of the stretching and locking structure of the viscous damper of the present invention under abnormal load.
Fig. 4 is a view B-B of fig. 3.
FIG. 5 is a schematic view of the compression locking structure of the viscous damper of the present invention under abnormal load.
In the figure: 1-left earring, 2-dynamic sealing element, 3-end cover, 4-static sealing element, 5-piston, 6-cylinder barrel, 7-piston rod, 8-locking cover, 9-inner sleeve, 10-outer sleeve, 11-locking device, 12-wear ring, 13-clamping groove, 14-right earring, 15-through hole and 16-thread plug; 11-1 to a plug, 11-2 to a spring and 11-3 to a snap ring.
Detailed Description
For convenience of description, the description of the relative position of the components (e.g., up, down, left, right, etc.) is described with reference to the layout direction of the drawings, and does not limit the structure of the patent.
As shown in fig. 1 to 5, a viscous damper includes a cylinder 6, a piston assembly disposed in the cylinder 6, a hollow inner sleeve 9, and a hollow outer sleeve 10. The piston assembly comprises a piston 5 slidable in a cylinder 6, and a piston rod 7 extending from the piston 5. The piston 5 divides the cylinder barrel 6 into closed chambers, and damping holes which can enable the closed chambers to be communicated are formed in the piston 5.
And end covers 3 and locking covers 8 for locking the end covers 3 are arranged at two ends of the cylinder barrel 6. And a static sealing element 4 is arranged at the joint of the end cover 3 and the cylinder barrel 6. And dynamic sealing elements 2 are arranged in the contact areas of the two ends of the piston rod 7 and the end cover 3.
The left end of the piston rod 7 is fixedly connected with a left earring 1. The right end of the outer sleeve 10 is blocked by a threaded plug 16. The right earring 14 is fixedly connected with the plugging part of the threaded plug 16. The threaded plug is integrally formed with the right earring 14.
The left end of the inner sleeve 9 is fixedly connected with the right end of the cylinder barrel 6. The inner sleeve 9 is sleeved in the hollow cavity of the outer sleeve 10, and the inner sleeve 9 and the outer sleeve 10 can move relatively.
A locking device 11 which can stop the relative movement of the inner sleeve 9 and the outer sleeve 10 is arranged between the inner sleeve 9 and the outer sleeve 10. The locking device 11 makes the relative movement distance S1 of the inner sleeve 9 and the outer sleeve 10 not less than the displacement S2 of the piston 5 forced by the daily load, and S1 not more than the displacement S3 of the piston 5 forced by the abnormal load.
The locking device 11 comprises two clamping grooves 13 arranged around the outer wall of the inner sleeve 9 at intervals and an elastic stopping device arranged on the outer sleeve 10. The distance between the two card slots 13 is 2 times S1.
The elastic stopping device comprises a clamping ring groove arranged around the inner wall of the outer sleeve 10, a clamping ring 11-3 arranged in the clamping ring groove and a spring 11-2. The outer wall of the outer sleeve 10 is provided with a through hole 15 communicated with the snap ring groove. The spring 11-2 is arranged in the through hole 15. A plug 11-1 is arranged at the through hole 15. One end of the spring 11-2 is abutted against the snap ring 11-3, and the other end of the spring is abutted against the plug 11-1. In order to ensure that the snap ring 11-3 can be quickly clamped into the clamping groove 13 when passing through the clamping groove 13 and is tightly attached to the clamping groove 13. The wall of the card slot 13 is a slope, and the width of the bottom of the card slot 13 is smaller than that of the card slot opening. The lower end of the snap ring 11-3 is provided with a chamfer which has the same inclination with the wall of the clamping groove and can be matched with the wall of the clamping groove.
A wear-resistant ring 12 is arranged on the outer wall of the inner sleeve 9 and between the two clamping grooves 13 in a surrounding manner.
The arrangement area of the snap ring groove is located between the two snap rings 13. In the initial state, the arrangement area of the snap ring 11-3 is located at the right middle of the two clamping grooves 13.
In order to make the structure compact, the right end of the piston rod 7 can extend into the hollow cavity of the inner sleeve 9. The axes of the cylinder barrel 6, the piston rod 7, the inner sleeve 9 and the outer sleeve 10 are on the same straight line.
In the prior art, the values of S2 and S3 can be accurately calculated according to the application scenario of the damper, and are easily achieved by those skilled in the art. For example, the displacement amount S2 of expansion with heat and contraction with cold can be calculated from the change in temperature; from the minimum earthquake generated load S3 is calculated. The size of S1 was designed according to S2 and S3.
Under the daily load action states such as temperature change (see figure 1), the clamping ring 11-3 is positioned between the two clamping grooves 13 on the inner sleeve 9, the clamping ring 11-3 is in friction contact with the wear-resisting ring 12 with a low friction coefficient, only the inner sleeve 9 and the outer sleeve 10 move relatively, the piston rod 7 and the dynamic sealing element 2 do not rub, the sealing element is ensured to be still intact after the damper is used for a long time, the sealing element is protected, and the leakage risk of the viscous damper is reduced.
Under the action of abnormal loads such as earthquakes and the like, the generated displacement S3 is large and far exceeds S2, and the snap ring 11-3 is embedded into the clamping groove 13 on the inner sleeve 9 under the action of the compression spring 11-2 (see figures 3-5), so that the inner sleeve 9 and the outer sleeve 10 are integrated, relative motion does not occur any more, and the conventional viscous damper is formed. Under the drive of abnormal load, the piston rod 7 drives the piston 5 to reciprocate, damping force is generated, energy is consumed, and the normal function of the viscous damper is exerted.
Claims (8)
1. The utility model provides a viscidity attenuator, includes the cylinder, sets up the piston assembly in the cylinder, the piston assembly includes piston that can slide in the cylinder, follow the piston rod of wearing out, airtight cavity is separated into with the cylinder to the piston, is equipped with the damping hole that can make airtight cavity intercommunication on the piston, its characterized in that: the device also comprises a hollow inner sleeve and a hollow outer sleeve; the left end of the inner sleeve is fixedly connected with the right end of the cylinder barrel, the inner sleeve is sleeved in the hollow cavity of the outer sleeve, and the inner sleeve and the outer sleeve can move relatively;
a locking device which can stop the relative movement of the inner sleeve and the outer sleeve is arranged between the inner sleeve and the outer sleeve;
the locking device enables the relative movement distance S1 of the inner sleeve and the outer sleeve to be not less than the displacement S2 of the piston forced by daily load, and S1 to be not more than the displacement S3 of the piston forced by abnormal load.
2. The viscous damper of claim 1, wherein: the locking device comprises two clamping grooves which are arranged around the outer wall of the inner sleeve at intervals and an elastic stopping device arranged on the outer sleeve; in an initial state, the setting area of the elastic stopping device is positioned between the two clamping grooves; the distance between the two card slots is 2 times S1;
the elastic stopping device can be clamped into the clamping groove to force the inner sleeve and the outer sleeve to be relatively static.
3. The viscous damper of claim 2, wherein: the elastic stopping device comprises a clamping ring groove arranged around the inner wall of the outer sleeve, a clamping ring arranged in the clamping ring groove and a spring, a through hole communicated with the clamping ring groove is formed in the outer wall of the outer sleeve, the spring is arranged in the through hole, and a plug is arranged at the through hole;
one end of the spring is abutted to the clamping ring, and the other end of the spring is abutted to the plug.
4. The viscous damper of claim 3, wherein: wear-resisting rings are arranged on the outer wall of the inner sleeve and between the two clamping grooves in a surrounding mode.
5. The viscous damper of claim 3, wherein: the wall of the clamping groove is a slope surface, and the width of the bottom of the clamping groove is smaller than the width of the opening of the clamping groove;
the lower end of the clamping ring is provided with a chamfer which has the same inclination with the clamping groove wall and can be matched with the clamping groove wall.
6. The viscous damper according to any one of claims 1 to 5, characterized in that: the right end of the piston rod can extend into the hollow cavity of the inner sleeve, and the axes of the cylinder barrel, the piston rod, the inner sleeve and the outer sleeve are on the same straight line.
7. The viscous damper of claim 6, wherein: the two ends of the cylinder barrel are provided with end covers, a static sealing element is arranged at the joint of the end covers and the cylinder barrel, and dynamic sealing elements are arranged in the contact areas of the two ends of the piston rod and the end covers.
8. The viscous damper of claim 7, wherein: the left end of the piston rod is fixedly connected with a left earring; the right end of the outer sleeve is plugged, and a right earring is fixedly connected to the plugged part.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010468069.2A CN111577811A (en) | 2020-05-28 | 2020-05-28 | Viscous damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010468069.2A CN111577811A (en) | 2020-05-28 | 2020-05-28 | Viscous damper |
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| Publication Number | Publication Date |
|---|---|
| CN111577811A true CN111577811A (en) | 2020-08-25 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010468069.2A Pending CN111577811A (en) | 2020-05-28 | 2020-05-28 | Viscous damper |
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| CN (1) | CN111577811A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112554040A (en) * | 2020-12-03 | 2021-03-26 | 武汉二航路桥特种工程有限责任公司 | Bridge anti-seismic damper adaptive to daily operation load longitudinal displacement response |
| CN115789158A (en) * | 2022-11-10 | 2023-03-14 | 江苏工邦振控科技有限公司 | Constant-temperature viscous damper |
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| CN205421005U (en) * | 2016-03-25 | 2016-08-03 | 株洲时代新材料科技股份有限公司 | Viscous damper of installation adjustable length |
| CN207569132U (en) * | 2017-11-14 | 2018-07-03 | 智性科技南通有限公司 | A kind of pressure self-balancing fluid linking damper |
| CN109306659A (en) * | 2018-09-25 | 2019-02-05 | 中铁二院工程集团有限责任公司 | A kind of fluid viscous damper adding free inching gear |
-
2020
- 2020-05-28 CN CN202010468069.2A patent/CN111577811A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20050189186A1 (en) * | 2004-02-26 | 2005-09-01 | Zf Friedrichshafen Ag | Self-pumping hydropneumatic suspension strut unit |
| CN101315112A (en) * | 2008-07-22 | 2008-12-03 | 上海材料研究所 | Viscous damper with axial stop |
| CN101942868A (en) * | 2010-09-28 | 2011-01-12 | 株洲时代新材料科技股份有限公司 | Viscous damping limiting method with limiting device and viscous damper |
| CN103671677A (en) * | 2013-12-24 | 2014-03-26 | 北京九州一轨隔振技术有限公司 | Viscous damper |
| CN204512282U (en) * | 2015-03-11 | 2015-07-29 | 常州鼎吉能源工程技术有限公司 | A kind of two rod hydraulic damper |
| CN205421005U (en) * | 2016-03-25 | 2016-08-03 | 株洲时代新材料科技股份有限公司 | Viscous damper of installation adjustable length |
| CN207569132U (en) * | 2017-11-14 | 2018-07-03 | 智性科技南通有限公司 | A kind of pressure self-balancing fluid linking damper |
| CN109306659A (en) * | 2018-09-25 | 2019-02-05 | 中铁二院工程集团有限责任公司 | A kind of fluid viscous damper adding free inching gear |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112554040A (en) * | 2020-12-03 | 2021-03-26 | 武汉二航路桥特种工程有限责任公司 | Bridge anti-seismic damper adaptive to daily operation load longitudinal displacement response |
| CN115789158A (en) * | 2022-11-10 | 2023-03-14 | 江苏工邦振控科技有限公司 | Constant-temperature viscous damper |
| CN115789158B (en) * | 2022-11-10 | 2023-10-31 | 江苏工邦振控科技有限公司 | Constant temperature type viscous damper |
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