CN201448440U - Ship sealing device insensitive to the deep sea pressure - Google Patents
Ship sealing device insensitive to the deep sea pressure Download PDFInfo
- Publication number
- CN201448440U CN201448440U CN2009200479754U CN200920047975U CN201448440U CN 201448440 U CN201448440 U CN 201448440U CN 2009200479754 U CN2009200479754 U CN 2009200479754U CN 200920047975 U CN200920047975 U CN 200920047975U CN 201448440 U CN201448440 U CN 201448440U
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- spring seat
- ring
- stationary ring
- sealing device
- rotating
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Abstract
The utility model relates to a ship sealing device, particularly relates to an improved ship deep sea sealing device insensitive to the deep sea pressure, which comprises a pneumatic sealing device, an oil lubrication sealing device, a rotating ring seat surrounding and fixedly connected to a shaft sleeve, a rotating ring mounted at the end part of the rotating seat, a spring seat surrounding the shaft sleeve and fixedly connected to the ship body, and a mechanical sealing device formed by a stationary ring which is sleeved on the spring seat and connected with the spring seat in a sliding way in the axial direction thereof, wherein pre-tightening springs are uniformly distributed in the spring seat in the circumferential direction, the two ends of the pre-tightening spring are in contact with the stationary ring and the spring seat respectively, the rotating and the stationary rings are arranged oppositely to form an end face seal pair, and the diameter of the sleeved part of the stationary seal ring and the spring seat is larger than the external diameter of the shaft sleeve, but smaller than the external diameter of the ring-like contact surface of the rotating and the stationary rings multiplied by 1.2. The utility model can balance automatically the axial pressure acted by the sea on the two sides of the stationary ring to integrate the rotating ring with the stationary ring closely, thereby improving the sealing effect.
Description
Technical field
The utility model relates to ship sealing device, relates in particular to the improvement of ship deep-sea sealing device.
Background technique
Ship sealing device is used to prevent that seawater from entering hull or device interior from the boats and ships transmission shaft, the quality of its sealability directly has influence on the safe operation of boats and ships, it is the important component part of boats and ships, particularly ocean engineering operation boats and ships need place, deep-sea, 65 meters left and right sides enforcement operation under water sometimes, and are high especially to the requirement of seal arrangement sealability.
When boats and ships especially ocean engineering boats and ships deep ocean work, static pressure is very big under water for it, only depend on the lubricated sealing device of oil sealing, its lip-type packing is easy to distortion, cause seal failure, so ship sealing device is generally by mechanical seal device, pressurized seal device, lubricated sealing device of oil constitutes, wherein mechanical seal is that a kind of usefulness solves the device that seals between transmission shaft and the body, it relies on elastic element to moving, the pretension of stationary ring end face seal pair and reach the axial end seal arrangement of sealing, the primary element that constitutes mechanical seal has: the end face seal pair of being made up of rotating ring and stationary ring, elastic element, secondary seal, driving component, rotation preventing device and fastening piece.
Mechanical seal device is the sealing of first road, stop seawater to be invaded, lubricated sealing device of oil is the sealing of second road, stops the seawater that is leaked by mechanical seal device to enter in the ship, and the sealability of boats and ships is born jointly by mechanical seal device and lubricated sealing device of oil and guaranteed.Pressurized seal device is not worked at ordinary times, has only when other seal failure, just starts pressurized seal device, and the opening air bag is tightly encircled transmission shaft (or axle sleeve), stops seawater to enter in the ship.
In the present mechanical seal device, spring seat is encircled axle sleeve or transmission shaft and is fixed on the hull, and stationary ring is socketed on the spring seat, and is located by the guide pillar of axial installation, stationary ring can only relatively not rotated between stationary ring and the spring seat along the spring seat axial slip.Preloading spring is installed in the spring seat, and the two ends of preloading spring contact with stationary ring with spring seat respectively.Rotating seat is encircled axle sleeve and is fixed on the axle sleeve, and the end of rotating seat is equipped with the rotating ring around axle sleeve, and rotating ring and stationary ring are oppositely arranged, and constitutes the end face seal pair, and stationary ring is pressed on the rotating ring under the elastic force effect of preloading spring vertically, thereby plays seal action.Because spring seat, rotating seat, rotating ring, stationary ring are the parts of sealing, thereby the outer surface of they and contact with sea water all is subjected to the pressure of seawater, wherein rotating seat and rotating ring are owing to being fixed together with axle sleeve, so rotating seat and rotating ring can axial displacement not take place because of seawater pressure; Spring seat is owing to be fixed on the hull, can axial displacement not take place because of seawater pressure, and the area of two end faces of stationary ring both sides and contact with sea water is unequal, the seawater pressure that is born is also unequal, because stationary ring is socketed in the spring seat, the area of side that stationary ring contacts with rotating ring and contact with sea water part is greater than the area of stationary ring opposite side and contact with sea water part, thereby the direction of making a concerted effort of the seawater pressure that is subjected to of stationary ring is pointed to spring seat vertically, promptly the direction with preloading spring elastic force is opposite, this makes that the stationary ring of formation end face seal pair and the contact pressure of rotating ring are weakened, especially in the underwater propeller of ocean engineering boats and ships, sometimes need 65 meters depths operations under water, the pressure that huge deep-water pressure will make stationary ring act on vertically on the rotating ring end face is seriously undermined, even cause mechanical seal leakage, cause major accident, even increase the contact pressure of rotating ring and stationary ring from aspects such as the [coefficient of that increases spring and number of springs, but because deep-water pressure is excessive, these measures often produce little effect, directly cause the sealability of whole ship sealing device to descend, still do not have good solution at present.
The model utility content
At the above-mentioned deficiency of existing in prior technology, technical problem to be solved in the utility model is that a kind of ship sealing device that not influenced by deep-water pressure will be provided, its energy autobalance seawater eroding makes rotating ring and stationary ring good fit in the axial pressure of stationary ring both sides, improves sealing effect.
In order to solve the problems of the technologies described above, the ship sealing device that the utility model is not influenced by deep-water pressure, comprise pressurized seal device, lubricated sealing device of oil and mainly by encircling axle sleeve and being fixed in rotating seat on the axle sleeve, be installed in the rotating ring of this rotating seat end, the mechanical seal device of encircling described axle sleeve and being secured to the spring seat on the hull and being socketed on this spring seat and constituting with stationary ring that this spring seat slidably links together vertically, the edge circumferentially is evenly equipped with preloading spring in the described spring seat, the two ends of this preloading spring contact with described spring seat with described stationary ring respectively, described rotating ring and described stationary ring are oppositely arranged and constitute the end face seal pair, and the diameter of described stationary ring and described spring seat socket part is greater than the external diameter of described axle sleeve and less than 1.2 external diameters that multiply by the annular contact surface of described rotating ring and described stationary ring.
After adopting such scheme, because the diameter of stationary ring socket spring seat part is greater than the external diameter of axle sleeve and less than 1.2 external diameters that multiply by the annular contact surface of rotating ring and stationary ring, thereby the side that contacts with preloading spring of stationary ring and the area of contact with sea water increase greatly, the seawater pressure that this side is born (direction is pointed to rotating ring by stationary ring vertically) also increases greatly, diameter by choose reasonable spring seat and stationary ring socket part, and consideration rotating ring external diameter factor, can make the suffered seawater pressure in stationary ring both sides equal substantially, roughly mutual balance, make the contact pressure of rotating ring and stationary ring not be subjected to the influence of seawater pressure substantially, guaranteed the stable of mechanical seal device and whole ship sealing device sealability.
When the diameter of stationary ring and spring seat socket part equaled the external diameter of annular contact surface of rotating ring and stationary ring, the seawater pressure of stationary ring both sides differed almost nil, and effect is best.
The diameter of stationary ring and spring seat socket part equals 1.2 when multiply by the external diameter of annular contact surface of rotating ring and stationary ring, and the seawater pressure of stationary ring both sides is more or less the same, and the sealability of mechanical seal device is not had big influence.
General in the spring seat along circumferentially being evenly equipped with 6～12 preloading springs.
Description of drawings:
Below in conjunction with the drawings and specific embodiments the ship sealing device that the utility model is not influenced by deep-water pressure is described in further detail.
Fig. 1 is that the ship sealing device that the utility model is not influenced by deep-water pressure is applied to the structural principle schematic representation that ocean engineering boats and ships electric plating propulsion transmission shaft seals.
Embodiment
Among Fig. 1, the ship sealing device that the utility model is not influenced by deep-water pressure is made of lubricated sealing device of oil 9, pressurized seal device 8 and mechanical seal device, and wherein mechanical seal device is installed near propeller cavitation one side, in the middle of pressurized seal device 8 is installed in.The end face seal pair that mechanical seal device mainly is made of rotating ring 4 and stationary ring 5, spring seat 7, preloading spring 6, rotating seat 3 etc. constitute.
Axle sleeve 1 is fixedly connected and be wrapped in the outer surface of transmission shaft 10, spring seat 7 is encircled axle sleeve 1 and is fixedly mounted on the hull, stationary ring 5 is socketed on the spring seat 7 and with spring seat 7 and slidably links together vertically, stationary ring 5 is equipped with cylindrical guide pillar 12 vertically with spring seat 7 adjacent sides, be processed with axial guide pillar slide opening 11 with guide pillar 12 corresponding positions on the spring seat 7, guide pillar 12 stretches in the guide pillar slide opening 11, and can in guide pillar slide opening 11, slide vertically, thereby make stationary ring 5 and spring seat 7 be slidingly connected vertically, do not relatively rotate between stationary ring 5 and the spring seat 7, only endwisely slip, 6 preloading springs 6 are installed in the spring seat 7, the two ends of preloading spring 6 contact with spring seat 7 with stationary ring 5 respectively. and rotating seat 3 is fixed together by setscrew nut 2 and axle sleeve 1, the end of rotating seat 3 is embedded with the rotating ring 4 that macromolecular material is made, rotating ring 4 is oppositely arranged with stationary ring 5 and constitutes the end face seal pair, stationary ring 5 is close on the end face of rotating ring 4 under preloading spring 6 elastic force effects vertically. and the diameter of stationary ring 5 and spring seat 7 socket part equals the external diameter of the annular contact surface of rotating ring 4 and stationary ring 5, when electric plating propulsion is operated in the deep-sea, because stationary ring 5 both sides equate with the area of contact with sea water part, the seawater pressure that bear stationary ring 5 both sides also equates, eliminated the deficiency of seawater pressure weakening preloading spring 6 elastic force, no matter any under water depths can both reach and adhere to specification to make the sealing of mechanical seal device, guarantees that the sealability of mechanical seal device and whole ship sealing device is unaffected.
Above-mentioned mode of execution only is the utility model one of mode of execution preferably; wherein the diameter of stationary ring and spring seat socket part not only is confined to equal the external diameter of the annular contact surface of rotating ring and stationary ring; also can equal 1.2 external diameters that multiply by the annular contact surface of rotating ring and stationary ring; can also be slightly less than the external diameter of the annular contact surface of rotating ring and stationary ring, all fall into protection of the present utility model so long as multiply by at axle sleeve external diameter and 1.2 between the external diameter of annular contact surface of rotating ring and stationary ring.
Claims (3)
1. the ship sealing device that not influenced by deep-water pressure, comprise pressurized seal device (8), lubricated sealing device of oil (9) and mainly by encircling axle sleeve (1) and being fixed in rotating seat (3) on the axle sleeve (1), be installed in the rotating ring (4) of this rotating seat (3) end, the mechanical seal device of encircling described axle sleeve (1) and being secured to the spring seat (7) on the hull and being socketed in that this spring seat (7) is gone up and constituting with stationary ring (5) that this spring seat (7) slidably links together vertically, the edge circumferentially is evenly equipped with preloading spring (6) in the described spring seat (7), the two ends of this preloading spring (6) contact with described spring seat (7) with described stationary ring (5) respectively, described rotating ring (4) and described stationary ring (5) are oppositely arranged and constitute the end face seal pair, and the diameter of described stationary ring (5) and described spring seat (7) socket part is greater than the external diameter of described axle sleeve (1) and less than 1.2 external diameters that multiply by described rotating ring (4) and the annular contact surface of described stationary ring (5).
2. the ship sealing device that not influenced by deep-water pressure according to claim 1 is characterized in that: the diameter of described stationary ring (5) and described spring seat (7) socket part equals the external diameter of the annular contact surface of described rotating ring (4) and described stationary ring (5).
3. the ship sealing device that not influenced by deep-water pressure according to claim 1 is characterized in that: the edge circumferentially is evenly equipped with 6 described preloading springs (6) in the described spring seat (7).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200479754U CN201448440U (en) | 2009-08-24 | 2009-08-24 | Ship sealing device insensitive to the deep sea pressure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200479754U CN201448440U (en) | 2009-08-24 | 2009-08-24 | Ship sealing device insensitive to the deep sea pressure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201448440U true CN201448440U (en) | 2010-05-05 |
Family
ID=42553156
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009200479754U Expired - Fee Related CN201448440U (en) | 2009-08-24 | 2009-08-24 | Ship sealing device insensitive to the deep sea pressure |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201448440U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102313021A (en) * | 2011-09-22 | 2012-01-11 | 丹东克隆集团有限责任公司 | Mechanical sealing device for integrated water seal |
-
2009
- 2009-08-24 CN CN2009200479754U patent/CN201448440U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102313021A (en) * | 2011-09-22 | 2012-01-11 | 丹东克隆集团有限责任公司 | Mechanical sealing device for integrated water seal |
| CN102313021B (en) * | 2011-09-22 | 2014-04-02 | 丹东克隆集团有限责任公司 | Mechanical sealing device for integrated water seal |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 224200, Zhenxing Road, Dongtai Economic Development Zone, Jiangsu 16-1, China Patentee after: Jiangsu Huayang Heavy Industry Co.,Ltd. Address before: 224200, Zhenxing Road, Dongtai Economic Development Zone, Jiangsu 16-1, China Patentee before: Jiangsu Huayang Heavy Industries Co., Ltd. |
|
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100505 Termination date: 20130824 |