KR860001696B1 - Stern tube real device - Google Patents

Abstract

The stern tube seal device has an annular case member arranged in outer periphery of a shaft. A gap between both the members is sealed in multiple stages by using a number of seal members such as a segment seal member, a lip seal member and the like. Pressurised gas is fed at the rear of the segment seal member which forms one of these seal members to enhance a seal effect by pressure of the gas.

Description

Stern Tube Sealing Device

1 is a half cross-sectional view of the stern tube sealing apparatus according to the first embodiment.

2 is a half cross-sectional view of the stern tube sealing apparatus according to the second embodiment.

3 is a half cross-sectional view of the stern tube sealing apparatus according to the third embodiment.

4 is a cross-sectional view of an essential part of the stern tube sealing apparatus according to the fourth embodiment.

5 is a half cross-sectional view of the stern tube sealing apparatus according to the fifth embodiment.

Fig. 6 is a sectional view of an essential part of the stern tube sealing apparatus according to the sixth embodiment.

7 is a half sectional view of the stern tube sealing apparatus according to the seventh embodiment.

8 to 10 are cross-sectional views of the main parts of the stern tube sealing apparatus according to different embodiments, respectively.

* Explanation of symbols for main parts of the drawings

2: shaft 5, 6, 7, 8: annular case member

12,17: sealing member 27: pressure fluid supply line (mechanism)

The present invention relates to a stern tube seal device.

One of the conventional seal devices of this kind, which has not been made until now, is provided with a number of lip seals installed in close contact with the shaft and sliding about the shaft, or mechanical seals are installed to leak seawater into the machine (ship). It has been designed to prevent both leakage from entering and leaking lubricant (bearing oil) out from the ship. However, in these prior arts, the sealing was dependent on the sliding portion formed between the reel seal and the circumferential surface of the shaft or the sliding portion of the mechanical seal. After long periods of operation, the sliding parts wear or deform, which reduces the seal's performance and creates the risk of lubricating oil spilling out of the ship and contaminating the sea.

Considering the above problems, the stern tube sealing device is designed to increase durability, including sealing performance against sea water and lubricants, prevention of slurry, and the action of preventing leakage of lubricants from contamination of the sea. It is an object of the present invention to provide.

In order to achieve the above object, the stern tube sealing device according to the present invention is installed in the annular clearance formed between the annular case member is formed on the outer periphery of the shaft, and the seal member is formed between the shaft and the case member for seawater and lubricating oil. It forms a multi-stage seal part, and pressure fluid is supplied to the seal part to increase the sealing effect by the pressure of the fluid.

Although the present invention has been briefly described and described, still other objects and novel features of the invention will become fully apparent from the detailed description given hereinafter in connection with the embodiments according to the accompanying drawings. However, the drawings are only for showing the embodiments to be used for the purpose of understanding the present invention is not limited by them.

First, a description will be given of a stern tube sealing apparatus according to a first embodiment of the present invention with reference to FIG. The stern tube sealing apparatus, denoted by the member number 1, seals between the shaft 2 fixed to the shaft or the shaft outside and the hull 3 into which the shaft is inserted. Reference numeral 4 denotes a part of the propeller installed at the end of the shaft.

The member number 5 is fixed to the hull through the gasket 9 by the first case member (casing), the second case member (or intermediate ring 6), the third case member (adapter ring 7), and the fourth case member ( The aft covers 8 are installed from the first case member 5 to the seawater A using the packing 10 and the like in this order.

These case members 5, 6, 7, and 8 are annular, of which only the second case member 6 has a hole having one large diameter, and the second case member 6 has one inner periphery. An annular recess 11 is formed, and the annular recess 11 is provided with a pair of segment seal members 12 and 12 therein. The segment seal members 12 and 12 are in intimate contact with the outer circumferential surface of the sleeve 2 by the adhesive force of the garter springs 13 and 13, and the segment seal member 12 on the left side of the segment seal member 12 is formed on both seal members ( 12, 12 is in close contact with the end of the third case member 7 by the saddle force of the coil spring 14 elastically installed on the corresponding surface, while the segment seal member 12 on the right side is the first case member. Make close contact with the end of (5).

The pin 16 fixed to the first case member 5 is inserted into the holes 15 and 15 concentrically drilled into both the members 12 and 12, thereby causing the segment seal members 12 and 12 to have a case member ( It becomes impossible to turn against 5).

The member No. 17 is fixed between the third and fourth case members by the rim seal member, and the annular rim 18 is in close contact with the outer circumferential surface of the sleeve 2 by the pressing force of the garter spring 19 Block seawater (A).

The reference numeral 20 denotes a mechanical lock seal provided on the lubricating oil B side of the segment sealing members 12 and 12, and the mechanical seal is a sliding ring 21 fitted to the inner circumferential surface of the shoulder of the first case member 5 toward the fixing part. ) And a sliding ring 24 fixed with a pin 23 with respect to the cover ring 22 fixed to the sleeve 2 on the rotating part side, and the two shafts are driven by driving as the shaft rotates. One seal sliding surface 25 is formed at the contact surface of the rings 21 and 24. The sliding ring 24 on the rotating part side is elastically pressed toward the sliding ring 21 on the fixed part side by the coil spring 26.

The member number 27 communicates from the hull side to the interior of the annular recess 11 which is blocked by the segment seal members 12 and 12 by means of a pressure gas supply mechanism, in which one pipeline is connected from the hull 3. It is provided through the first and second case members 5 and 6 so that the pressure gas is supplied into the annular post portion 11 by a supply device (not shown). The member 28 is formed separately from the pressure gas supply mechanism 27 as a recovery mechanism of the leaked fluid, and it is opened to the space between the segment seal member 12 and the mechanical seal 20, so that the Recover the leaking fluid entering the space. The stern tube sealing device 1 made as described above is for preventing seawater from leaking into the hull and lubricating oil B leaking out of the hull. In general, the pressure gas supply mechanism 27 and the leaking fluid recovery mechanism 28 are put into operation during sealing. On the other hand, the rim seal member 17 and the segment seal member 12 contribute to preventing the sea water (A) from leaking, in particular, the segment seal 12 is pressurized by the pressure gas coming into the annular recess 11 Since the sleeve 2 and the case member 7 are pressed strongly, the sealing effect of the seal portion is enhanced.

In addition, when the pressure of the pressure gas is higher, the pressure gas passes through the seal portion such that an opposite pressure exists in the space between the rim seal member 17 and the segment seal member 12, or the seawater pressure existing in the space. Will be in equilibrium. Further, when the pressure gas fills the space, back pressure is applied to the rim seal member 17 to cause the rim seal member 17 to be in an idling state (the force of close contact with the sleeve 2 disappears). Leave early wear or deformation of (17).

In this case, the rim seal member functions as a dust seal to prevent foreign matter from entering the ship, while when the pressure of the pressure gas is reduced, the rum seal member 17 is pressed against the pressure of the sea water to closely adhere to the sleeve 2. It makes contact and automatically serves as the primary seawater protection seal. On the other hand, with respect to the lubricating oil B, the mechanical seal 20 functions as a primary sealing portion that prevents the lubricating oil from leaking, and it is possible to completely prevent the lubricating oil from leaking out of the hull to the outside. This is in charge. When lubricating oil (B) enters the space between the mechanical seal (20) and the segment seal portion (12), the lubricating oil passes through the seal portion of the segment sealing member (12) and, together with the pressure gas entering the space of the hull, leaking oil The recovery mechanism 28 allows for low recovery and reuse.

The stern tube sealing device configured as described above can completely block both seawater A and lubricating oil B in the manner described above.

The following describes a second embodiment of the present invention with reference to FIG. Also in FIG. 2, the same member number as used in the first embodiment (FIG. 1) is used for the same member. In other words, reference numeral 2 is a sleeve, 3 is a hull, 4 is a propeller, 5, 6, 7, and 8 is a case member, 11 is a ring recess, 12, 12 is a segment seal member, 17 is a rim seal member, 27 is Pressure gas supply mechanism, and 28 are leak oil recovery mechanisms.

The stern tube sealing device 30 having the above members is mainly different from the first embodiment in the following points. That is, the fifth case member 31 is fixed to the inner circumferential portion of the shoulder portion of the first case member 5 and the second rim seal member 32 is fixed between the members 5 and 31. will be.

The sixth case member 33 is further fixed to the lubricating oil B side of the fifth case member 31, and the third segment seal member 54 is disposed in the space between the two members 31 and 33. It is installed as one float seal member.

The outer circumferential surface of the sleeve 2 of the segment seal member 34 is in intimate contact with each other by a garter spring 35 fixed to the outer circumferential portion of the segment seal member, and the pin is not shown with the fifth case member 31. By the coil spring 36 suppressed with respect to the sixth case member 33 is also in close contact with the end of the fifth case member 31.

From the fifth case member 31 to the first case member (3) so that the pipeline serving as the second leaked oil recovery mechanism 37 is opened into the space between the rim seal member 32 and the segment seal member 34. 5) stretched up to

The first and second leaking fluid recovery mechanisms 28 and 37 provide a confluence point of pipelines within the first case body 5 or the hull 3 to enable common use of suction recovery devices such as pumps, for example. Let's do it.

The stern tube sealing device 30 configured as described above has the same operation and seawater (A) prevention sealing effect as in the first embodiment. As for the lubricating oil B, the first seal portion is formed by the third segment sealing member 34. Even if there is lubricating oil leaking through this, the amount is only a very small amount.

In this manner, a sufficient sealing effect can be achieved by the rim seal member 32, and there is no great difficulty in recovering the lubricating oil on board by the leaked fluid recovery mechanism 37.

The following describes a third embodiment with respect to FIG. In this figure, the member number 42 represents an axis (including a sleeve covered on the side outer surface) and a screw, not shown, is provided on the left side thereof.

A case member 43 composed of the first to fifth members 44, 45, 46, 47, and 48 is disposed on the outer circumference of the shaft 42, and the hull 50 is provided using the packing 49 as a means. It is fixed at.

The member number 51 is an outer rim seal which is located on the inner circumference of the hole of the case member 43 and is fixed between the first case member 44 and the second case member 45, and is fixed by the fixing ring 52. The outer rim seal with the pressure receiving surface 51a faces the seawater A.

A backup ring portion 45a of the rim seal 51 for controlling the operation of the rim seal 51 is provided behind the second case member 45. Reference numeral 53 denotes an inner rim seal fixed between the fourth case member 47 and the fifth case member 48, and the inner rim seal provided with a fixing ring 54 and having a pressure 53a is Facing the lubricating oil B opposite the inner rim seal 53.

A backup ring 47a for the rim seal 53 is provided on the inner circumference of the fourth case member 47.

The inner diameter of the third case member 46 in the case member 43 is formed larger than the other four members 44, 45, 47, 48, in particular larger than the second and fourth case members 45, 47. , The annular ink portion 55 is formed on the inner circumference of the third case member 46, the annular ink portion 55 is provided with a flow ring seal 56 therein.

The ring ring 56 is liberated from the case member 43 as the knock pin 57 protruding from the fourth case member 47 is coupled to a cut 56a formed at one end thereof. Both ends and the inner circumferential surface thereof are provided at a slight distance from the outer circumferential surface of the second and fourth casing members 45.47 and the shaft 42 to form small gaps 58, 59, and 60.

The flow ring 56 has an annular groove 56b formed on the inner circumferential surface thereof, and the required number of through holes 56c penetrate the inner circumferential surface and the outer circumferential surface thereof.

Reference numeral 61 denotes a supply line of the pressure gas, which communicates with the annular recessed portion 55 partitioned by the flow ring seal 56 from the hull side, and the line connects the third and fourth case members 46 and 47. Through this, a pressure fluid is supplied to the annular portion 55 from a fluid supply device (not shown) provided in the ship.

The member 62 is a leaked fluid recovery line formed separately from the pressure fluid supply line 61, and the recovery line is opened to the space between the flow ring seal 56 and the inner rim seal 53, The leaking fluid flowing into the space can be recovered by a pump or the like (not shown).

In the stern tube sealing device 41 configured as described above, when the pressure fluid is supplied from the pressure fluid supply line 61 into the annular recess 55, the annular recess 55 is formed through the annular recess 55 and the through hole 56c. The annular groove 56b of the flow ring seal 56 communicating with 55 is filled with a pressure fluid, and the pressure fluid passes through the gaps 58, 59 and 60 and gradually into the spaces 63 and 64. It flows in. The pressure fluid flowing into the space between the outer rim seal 51 and the flow ring seal 56 in this pressure fluid is stored in the space 63, acting as a back pressure to the outer rim seal 51, and the rim seal ( The slip load between 51) and the outer circumference of the shaft 42 is reduced to prevent the inflow of seawater.

At this time, since the pressure fluid may flow out of the ship depending on the pressure, it is preferable that there is no fear of seawater pollution as the pressure fluid, and air is most preferable.

On the other hand, in the space between the inner rim seal 53 and the flow ring seal 56, the flow of pressure fluid flows further with the lubricating oil B leaking out of the inner rim seal 59, whereby the leaked fluid Recovered from the recovery line 62 into the ship.

In this manner, the flow ring seal 56 can play a sufficient role as the second seal for the rim seals 51 and 53 as long as the pressure fluid is supplied. If for some reason the supply of pressure fluid is interrupted, the flow ring seal 56 functions as a second seal of limited leakage type, to some extent in cooperation with the recovery mechanism by the leaked fluid recovery line 62. Achieve ring effect.

Therefore, in the sealing device 41 having the above-described structure, the outer rim seal 51 is pressed by the backside of the pressure fluid to reduce the sliding load between the rim seal 51 and the outer circumferential surface of the shaft 42. To improve the durability of the rim seal 51, which has been heavily worn in the past, to actively seal both seawater (A) and lubricating oil (B), and also to recover the lubricating oil (B) on board through the leaked fluid recovery line (62). There is no concern about sea pollution. 4 shows the main part of the fourth embodiment. In other words, the floating ring seal 56 is a double seal 65 whose rear surfaces correspond to each other.

The two seal members 66 and 67 are restrained by the common knock pin 68, and a required number of springs 69 are provided between the two seal members 66 and 67.

A fifth embodiment of the present invention will be described with reference to FIG. In this figure, reference numeral 72 designates an axis (including a sleeve fitted outwardly on the axis), on the left side of which a screw (not shown) is provided.

The case member 73 including the first to fifth members 74, 75, 76, 77, and 78 is installed on the outer circumference of the shaft 72 and is fixed to the hull 80 by the packing 79. .

The member number 81 is located on the inner circumference of the hole of the case member 73 and represents an outer rim seal contained between the first case member 74 and the second case member 75. The outer rim seal is attached to the fixing ring 82. Combined and installed opposite the seawater.

A back-up ring portion 75a for controlling the operation of the rim seal 81 is provided behind the second case member 75 with respect to the rim seal 81.

The member number 83 denotes a lubricating oil (B) which is located on the opposite side of the outer rim seal 81 because the inner rim seal between the fourth case member 77 and the fifth case member 78 is coupled to the fixing ring 84. It has a pressure receiving surface 83a facing toward).

The bag-down ring powder 77a with respect to the rim seal 83 is provided on the inner circumference of the fourth case member 77. The inner diameter of the third case member 76 among the case members 73 is made larger than the inner diameters of the other four case members 74, 75, 77, 78, especially the second and fourth case members 75, 77. An annular rainfall portion 85 is formed on the inner circumference of the third case member 76.

The member No. 86 is a pressure hollow ring made of rubber bonded to the annular recess 85. The hollow ring has a plurality of annular crests (three are shown in the drawing) which are continuously formed on the inner circumferential surface thereof. crest portion 86a, which acts as a sealing portion that comes into contact with the shaft 72 and drills a small number of fine holes 86d necessary (two are shown in the figure). The rough section 86b and the crest portion 86a and the hollow portion 86c are in communication with each other.

The member number 87 is a pressure drilled from the side of the hull toward the hollow portion 86c of the pressure hollow ring 86 to supply pressure fluid from the fluid inlet device (not shown) installed in the ship (not shown) to the hollow portion 86c. Indicates fluid supply line.

Part number 88 indicates a leaking liquid recovery line formed separately from the pressure fluid supply line 87, which is opened into the space between the pressure hollow ring 86 and the inner rim seal to enter the space. The leaked liquid is recovered by ship using a pump or the like not shown.

In the stern tube sealing device 71 configured as described above, if the pressure fluid is supplied from the pressure fluid supply line 87 to the hollow portion 86c of the pressure hollow ring 86, the pressure fluid is hollow. Filled in portion 86c and passed through a fine hole 86d to fill the space of a triangular cross section surrounded by the inclined surface of two adjacent crest portions 86a and the circumferential surface of shaft 72, so that the pressure and Balanced by the hollow portion 86c, the pressure-type hollow ring 86 comes into contact with the shaft 72 under low load.

If the pressure fluid is continuously supplied, the pressure fluid opens the seal portion between the pressure hollow ring 86 and the shaft 72 and flows to the balls 89 and 90.

The pressure fluid flowing into the space 89 between the outer rim seal 81 and the pressure hollow ring 86 is stored in the space 89 to act as a back pressure against the outer rim seal 81 so that the rim seal 81 ) And the sliding load between the outer circumferential surface of the shaft 72 to prevent the intrusion of sea water (A).

In this case, the pressure fluid is thought to flow out of the ship according to the pressure by pushing the rim seal 81, so selecting a pressure fluid such as compressed air, which does not cause a problem in terms of sea pollution, It is preferable to use. On the other hand, the pressure fluid flowing into the space 90 between the inner rim seal 83 and the pressure hollow ring 86 is leaked fluid recovery line with the lubricating oil B leaked from the inner rim seal 83, if any. It is recovered by ship from 88. In this way, the pressure-type hollow ring 86 can sufficiently perform the function of the second seal on the rim seals 81 and 83 as long as the pressure fluid is supplied.

Even if the supply of pressure fluid is stopped for some reason, the hollow ring acts as the second seal of the limited leakage type to cooperate with the function of the leaked fluid recovery line 88 to maintain the sealing effect to some extent. As a result, according to the sealing device configured as mentioned above, the outer rim seal 81 is subjected to the pressure of the back side by the pressure fluid, thereby reducing the sliding load between the rim seal 81 and the outer circumferential surface of the shaft 72 and thus greatly. It improves the life of worn rim seals (81) to seal the seawater (A) and lubricating oil (B) well, and recovers the lubricating oil (B) through the leaked fluid recovery line (88) to drain the pollutants of the seawater. Remove it.

6 shows an important part of the sixth embodiment. That is, the inner circumferential portion 86e of the pressure hollow ring 86 is made of synthetic rubber or fluorine resin having excellent wear resistance in order to increase wear resistance.

A seventh embodiment of the present invention will be described with reference to FIG. In FIG. 7, the stern tube sealing device indicated by the alternative member number 101 seals between the sleeve 102 coupled to the outside of the shaft (not shown) and the hull 103 into which the shaft is inserted. In order to do this, the hole opening of the hull 103 is provided.

Reference numeral 104 denotes a part of the propeller provided at the end of the shaft. In the stern tube sealing device, the member number 105 denotes a first casing fixed to the end of the hull 103 by a gasket 106, and a second casing (adapter ring) on the seawater B side of the first casing 105. 107 and the third casing (solid cover) are secured in an airtight state by an appropriate member such as a 0-ring 109 or the like. The inner circumferential surface of the second casing 107 is formed by the second casing 107 and the first casing 105 disposed on the back side, and the annular recessed portion 110 in which the segment seal 111 is installed therein is a sealed seal type. ) Is formed.

The segment seal 111 divided into several parts in the circumferential direction is fixed by the garter spring 112 installed on the outer circumference thereof and slides in close contact with the circumferential surface of the sleeve 102. It is in close contact with the wall surface 107a of the second casing 107 by the coil spring 113 provided on the back side.

Separate elements of the segment seal 111 are inhibited from rotating relative to the casing 105, 107 by pins not shown, which protrude from the first or second casing 105, 107. Reference numeral 114 denotes a rim seal secured between the second and third casings 107 and 108, which has a pressure receiving side 114a fixed by a garter spring 115 facing toward the sea. And it is sliding in close contact with the outer periphery of the sleeve (102). A back-loading portion 107b for controlling excessive deformation of the rim seal 114 is provided at the rear of the rim seal 114 of the second casing 107.

Reference numeral 116 denotes a mechanical seal installed at a position closer to the lubricating oil B side in the inner circumference of the hole of the first casing 105, which is engaged in the shoulder portion of the first casing 105 and has a zero ring. It is kept in airtight state by (118). The mechanical seal 116 is a sliding ring 117 on a fixed side where the rotation of the casing 105 is suppressed by a pin not shown, and a lid fixed to the sleeve 102 by a pin not shown. A ring 119 and a sliding ring 120 on the side of rotation rotated as the axis whose rotation is inhibited by the pin (not shown) rotates. The sliding ring 120 on the rotational side is pressed by the coil spring 121 to form a sealing sliding surface 122 on the surface in contact with the sliding ring 117 on the fixed side.

Reference numeral 123 denotes a pressure fluid supply line for supplying pressure fluid from the side of the hull 103 to the space 124 of the annular hole formed between the segment seal 111 and the mechanical seal 116. The pipeline is opened from the hull 103 to the space passing through the first casing 105, and a supply device (not shown) is provided in the hull 103.

The stern tube seal device 101 constructed as described above has a rim seal 114, a segment seal and a slurry contained in seawater and seawater, which is installed on the outer side of the mechanical seal 116 (sea side). (116) It prevents you from coming in.

In general, it should be noted that during sealing the feeder is driven to supply pressure fluid. That is, first, the rim seal 114 and the segment seal 111 serves to prevent the intrusion of seawater A. In particular, the segment seal 111 is a circumferential surface of the sleeve 102 and the wall surface of the second casing 107. 107a is pressed to increase the sealing effect. If the pressure of the pressure fluid exceeds a certain level with respect to the limited leakage segment seal 111, the pressure fluid flows backwards toward the rim seal 114, but the pressure fluid is balanced with the sea water to exhibit a sealing effect. . When the space between the rim seal 114 and the segment seal 111 is filled with the pressure fluid, the back pressure is applied to the rim seal 114 by the pressure fluid to balance the rim seal 114 with the seawater pressure. This prevents rapid wear and deformation due to sliding contact between the rim seal 114 and the sleeve 102. If the rim seal 114 also acts as a dust seal to prevent foreign matter from entering the vessel, the rim seal 114 is pressed against the sleeve 102 by sea water pressure if the pressure of the back pressure oil is reduced for some reason. It comes in contact with and automatically acts as the first seawater protection seal.

Since the pressure fluid is crushed by pressing the rim seal 114 according to the pressure size, it flows out of the ship. Therefore, even if the fluid leaks into the sea, it is preferable to use air, nitrogen gas, clean water, etc., which does not cause problems such as pollution. . On the other hand, the lubricating oil (B) is completely sealed by the mechanical seal 116 with improved durability sealing characteristics by the above-described structure.

8 to 10 show modified embodiments of the present invention, in which instead of the limited leaky segment seals described in the previous embodiments, a floating unit (not divided in the circumferential direction) is floating. ) Ring seal 125 (FIG. 8), end type rubber seal 127 (FIG. 9) or hollow pressure ring 130 (FIG. 10) is used. In other words. The floating ring seal 125 shown in FIG. 8 is suppressed from rotation by pins (not shown) provided on the first or second casings 105 and 107 and pressed by the coil spring 126. It is in contact with the wall surface 107a of the second casing 107 and has a fine clearance with respect to the circumferential surface of the sleeve 102, so that the pressure fluid is sealed by a limited leakage method.

The end type rubber seal 127 shown in FIG. 9 is pressed onto the rubber seal 102 by the garter spring 128 to form a sealing sliding surface against the wall surface 107a of the second casing 107. The fluid is then sealed by the back surface. The cleaning and flushing line 129 is opened from the second casing 107 to the annular groove 127a formed on the surface. This washing and lubrication line is separated from the pressure fluid supply line 123 and clean water is used as a supply fluid to provide lubrication on the sliding surface. The hollow pressure ring 130 shown in FIG. 10 is installed in close contact with the first and second casings 105 and 107, as if filled in the annular recess 110, and the pressure against the hollow portion 130a. The compressed air is expanded from the fluid supply line 123 or is provided separately from the line 131 which is separately installed to expand the hollow compression ring in the inner diameter direction so as to come into close sliding contact with the circumferential surface of the sleeve 102.

The use of the compressed hollow ring 130 may control the amount of compressed air so that the state of close contact with the circumferential surface of the sleeve 102 may be changed to adjust the amount of leakage of the pressure fluid. Typically, the inner circumferential surface portion of the hollow ring 130 made of synthetic rubber is made of a sliding fluid material such as fluorine resin to increase wear resistance.

In the stern tube sealing device of the present invention, as described above, the segment sealing member, the rim sealing member, the mechanical direct sealing member, and the like form a multi-sealing portion, and the pressure of the pressure fluid is also used. Therefore, the excellent sealing performance of both seawater and lubricating oil is exerted, as well as the rim seals installed near the seawater, the load is reduced by the pressure of the pressure fluid and the damage to the mechanical seal is applied. Increase long life.

In addition, according to the stern tube sealing apparatus of the present invention, sea pollution is prevented, which effectively solves various problems of pollution caused by international problems in recent years.

While preferred embodiments of the invention have been described and described, it will be apparent that many variations to the invention are possible without departing from the principles of the invention.

Accordingly, all modifications that can substantially achieve the effects of the present invention using structures which are substantially the same as or corresponding to the present invention should be included in the scope of the present invention by the appended claims.

Claims (6)

An annular case member is installed on the outer circumference of the shaft, and a plurality of sealing members are formed in a space formed between the shaft and the case member to form a multi-sealing portion for seawater and lubricating oil, and the pressure fluid as the sealing portion. Stern tube sealing device, characterized in that the pressure fluid supply line for supplying the provided. An annular recess having a segment seal member provided in the present invention is provided on an inner circumferential surface of the hole of the case member, and a supply mechanism for supplying a pressure gas to the annular recess closed by the segment seal is provided. And a rim seal member is installed on the seawater side of the segment seal member while a mechanical seal, packing or another flow seal member is installed on the lubricating oil side of the segment seal member. The mechanical seal for sealing a portion between the case member and the circumferential surface of the shaft is provided at a position closer to the belly from the inner circumference of the case member, wherein the annular recess is formed on the inner circumferential surface of the case member. A confined leak-tight seal formed on the belly of the mechanical seal and in sliding contact with the circumferential surface of the mechanical seal is coupled in the annular recess, and an annular space between the constrained leak seal and the mechanical seal to supply pressure fluid. Stern tube sealer, characterized in that the pressure fluid supply line is provided open. The ring recess of claim 1, wherein a plurality of rim seals are fixed to the inner circumference of the hole of the case member, and the annular recess having the seal member installed therein is formed on the inner circumferential surface of the hole of the case member at an intermediate point of the plurality of rim seals. And a pressure fluid supply line for supplying a pressure fluid to the seal member. The stern tube sealing apparatus according to claim 4, wherein a flow ring seal is used as the seal member. The pressure member according to claim 4, wherein a plurality of crest portions are continuously formed on the inner circumferential surface of the pressure hollow ring as the seal member, and a pressure hollow ring for forming a seal portion is used. Stern tube sealing device, characterized in that the holes are drilled in the trough portion.

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