JPS5986755A - Sealing device for oil pressure - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] TECHNICAL FIELD The present invention relates to an oil-based 11-nor device.

The known hydraulic system has a component (4) which has a relative rotational movement, and the rotating component has a rotating member with a concave i13 on the inside and a rotary member similar to this but with a rotational speed. and a rotating member equipped with a sealing device that protrudes slowly into the recess.The recess is located on the -L flow side i/C II
It is formed between μ and the weir 1Lllll downstream, into which the /Ik rod is added. This liquid is supplied by the hydraulic system 41.
11+j is held in the four parts by the rubbing centrifugal force VC, and the material 111~ that constitutes the sealing device enters radially into this liquid, causing gas tit,
This is to avoid overflowing the ml/l rule.

The above expressions "upstream" and "T flow" refer to the upstream and "F" flows in the direction in which the upper air gas flows. Below υ above!
The +11t of l-11111 is sufficiently eroded in the radial direction, and the centrifugal force applied to the liquid in the river between the first rule of F flow and the second self-sealing device causes the above-mentioned sealing device member to Since the pressure is greater than the pressure applied to the liquid upstream, the sealing member acts as a barrier and completely blocks the flow of the gas.

The driving force generated by the rotation of the liquid in the recess is generated by friction between the liquid and the wall surfaces of the four parts and internal friction of the liquid itself. Therefore, for all liquids, a slip coefficient is used to prevent the liquid from reaching a maximum angular momentum that would result in a loss of pressure due to centrifugal force.

Therefore, when the pressure of the gas flow is relatively low, the sealing device as described above is used, for example, 0.0352 kg/d (5 psi).
) to 0.703kl? /d (10P81), a short +1 is provided to perform a proper sealing action. Further, there is a very serious problem in using the above-mentioned sealing device for sealing between constituent members that undergo relative rotational movement similar to rotation.

If the pressure of the gas is higher, for example 4,219 kg
/cr/! (60 ps quantity) to 5-625 kgl
In the case of cr& (80 ps +), it is necessary to apply a larger centrifugal force to the liquid, and the height of the weir on the downstream side in the radial direction must be increased accordingly, but there are spatial constraints. Therefore, it is not always possible to make Ill as crystalline as necessary.

The components! There is no example of the above-mentioned rotation being used in the case of rotation in opposite directions, and it is because the surface of the weir and the constituent members of the sealing device rotate in opposite directions. Rotational speed of the faster axis 1
It has been believed that this is due to the lower average rotational speed and lower efficiency compared to &.

Another problem is that if the 7-hole of the sealing device is ruptured, for example, after the pressure of the gas has stabilized at the maximum pressure, the liquid temporarily decreases due to an exception. Even if the liquid is replenished downstream of the sealing device, the formation of a layer of liquid in the recess is prevented by the airflow formed by the gas passing through the sealing member of the sealing device.

SUMMARY OF THE INVENTION An object of the present invention is to provide a hydraulic sealing device that can at least partially solve the problem described in L and sufficiently improve sealing efficiency.

According to the invention, the sol device is located between two components having a relative rotational movement, including four parts, a liquid supply device,
It consists of a sealing part and a pump, and the above four parts are formed between the upstream side of the component with a faster rotation speed and the downstream side of the weir, and this component The liquid supply device supplies the liquid to the concave portion, and the sealing member is located on the component having a slower rotational speed IW among the components. The length of the pump is long enough to be fully immersed in the liquid held by centrifugal force in the four parts; The liquid is taken in from the recess, driven sufficiently to the speed of the component, and discharged to the farthest part in the radial direction of the recess.

This device applies centrifugal force to most of the liquid by driving it up to the rotational speed of the components on the high speed side, especially in a curved sealing device for components rotating in opposite directions. The effects of rotation of components rotating in opposite directions can be reliably offset. By installing the liquid supply device and sending one fertilizer liquid to all the intake ports of the pump, when the liquid in the pool device temporarily decreases, the pump will supply the liquid to the four parts. +4 can be applied to maximize the pressure due to centrifugal force, thereby reducing the amount of gas flowing beyond the sealing member.

The above-mentioned pump rJ: ,, I- It is preferable to use a structure using vanes or a porous structure so as to sufficiently drive the liquid-resistant pump.

As part C of the embodiment of the present invention, the above-mentioned two components having relative rotational motion are two shafts of a gas turbine engine that rotate in opposite directions, and the air between these two shafts is A platform using engine oil as the liquid for sealing the flow will be described.

Hereinafter, an embodiment of the present invention will be explained with reference to Fig. F1.

In FIG. 1, shafts 1 and 2 are paired and rotate in opposite directions, with the outer shaft rotating faster when viewed in the diametrical direction. The inner surface of this outer shaft is radially provided with four sections 3, which recesses are formed in the upstream weir 4 and the downstream weir 111.

The expressions "upstream" and "downstream" refer to the direction of gas flow between the axes, i.e. the direction indicated by arrow A in the figure;
It represents the upstream and downstream of .

The inner shaft rotates slowly and has an annular fin 6 which projects radially outward from the surface of the shaft and into the recess formed by the weir. It has a length that allows it to be fully immersed in the retained liquid. This liquid is supplied by a tube 7 into the recess from the downstream end.

Upper internal gas (air) flows in the direction of arrow A through the annular space between the shafts, and this air flow passes through the tip of the sealing fin 6, and between this fin 6 and the liquid (oil). It passes through a sealing device that is formed. In connection with such a structure, the weir 5 on the downstream side is set to a sufficiently deep depth <17, thereby increasing the depth of the liquid between the weir 5 and the fins 6, so that when centrifugal force is applied to the weir 5, The centrifugal force is made larger than the pressure of the liquid upstream of the fin 6 (this pressure is generated by the air 1111 upstream of the fin 6 pressing the liquid upstream of the fin 6), thereby The overall structure is such that air on the upstream side of the fins 6 is prevented from leaking.

Since the shaft rotates in the opposite direction, viscosity tli; is applied to the surfaces of the four parts and acts as a driving force. This phenomenon lowers the average velocity of the liquid in the four parts, so if the rate of decrease in this average velocity IW is expressed as a "slip coefficient", this slip coefficient becomes very sharp. In order to eliminate this slippage, a pump 9 having vanes is provided.
It is disposed between the upstream side of I 5 and the wall lO of shaft 2 extending radially inward from this weir 5. The liquid supply pipe 7
In this embodiment, the liquid is shown to be poured into the downstream end of the recess, but this liquid supply pipe is used to pour the liquid into the radially inner end of the vane constituting the fluid inlet of the pump 9. arranged for injection. Is the liquid injected above the month above? The liquid is discharged from the radially outermost end of the blade of the pump to the radially outermost end of the four parts, and this discharged liquid enters the annular passage 12 formed adjacent to the light height part of the fin 6. . If the pump 9 is shifted so that all the liquid overflowing from the weir 5 is sucked in by the radially inner end of its blade, a liquid circulation flow passing through the recess is formed, and the liquid flows from the annular passage 12. The wall 14 of this ring path 12
It flows radially inward through the gap 13 between the L fin 6 and the L fin 6 at a high speed. This circulating flow of liquid serves to remove the liquid flowing into the pump 9, and also serves to replenish the pump 9 with the liquid when the liquid is not discharged from the liquid supply pipe. In this way, the pump 9
so that the liquid can be driven at the rotational speed of the shaft 2. In this way, the pressure caused by the centrifugal force can be maximized by at least appropriately selecting the type of liquid.

Shichikikan Inuji 12? IHJ between the fin 6 and the bottom of the upper part 3! By making it equal to 4j, the pressure due to the centrifugal force generated in the liquid at the same depth as this gap can be maximized.

In this way, the frictional force between the four-part surface and the four-part surface, which is 1=- in the sealing device and only acts to drive the liquid, is reduced to l? W-1- Since the slip coefficient is pyro in all parts of the seal 3A, the seal can be made tight by the pump. Therefore, even if the radial depth of the liquid is /lA<, the pressure of the /l corpse can be increased.

6 r'-, which has an axis that rotates q, and in turn anti-k 1 force rotation.
Star pin 7-le 1i? The liquid used in step 4 is engine oil, and the engine oil is stirred by the fins rotating in opposite directions to raise its temperature.

Therefore, in order to prevent this engine oil from boiling or foaming, it is necessary to constantly supply cold engine oil to the recesses 1-1 and 1-1. 1. Passing the air through the sealing device. ) (This is to make the engine oil overflowing from the upstream drain 4 flow back to the drain on the second flow side of the engine through a hole 8 provided at a friil+ upstream of the engine oil pump Ill 4.

Under normal operating conditions of the engine, the pressure of the sealed air is closely related to the speed IW of the engine, so when operating at low speeds, that is, when the pressure due to the centrifugal force of the engine oil is low, the seal portion is closed. The pressure of the air passing through is low. However, if the supply of the engine oil is interrupted and the seal is broken after the air pressure becomes extremely high for some reason, the tip of the fin 6 that stops the engine oil should be moved at high speed. This air flow prevents engine oil from entering the four parts and sufficient recovery of pressure due to centrifugal force when the engine oil supply is resumed. On the other hand, if a seven-wheel device with an auxiliary pump according to the present invention is used, the auxiliary pump rotates the engine oil to the maximum rotational speed, causes the engine oil to flow into the recess, and causes the engine oil to flow far away. Since the pressure by the 11 J force is maximized, the geometry of the self-sealing device 1 can be maintained.

I ni ha self section > J il+'jl+! Sole mounting for J-ru [Another fruit of the hood! Blood 1"l 5r 'I'+
A concrete example is shown in Figure 2. Each part of this sealing device'/〈'
- (1' Ij 1., identification ([1 number is the same as in Fig. 1. In this example, the radial depth of the downstream weir is 1, [- marked bomb 9 Lower f & farthest end wall 10
The depth is deeper than the radial depth of 1, and all the engine oil to be supplied to the sealing device is supplied to the suction port of the pump 1.
-ru. 1- The IQ-shaped passage 12 is connected to the shaft 2 and the cylindrical side plate 1.
The side plate 15 is formed between the fins 6 and 5, and the side plate 15 is
−oV, extended to ll1ll l/, superior eye circular tract 1
2, engine oil is discharged directly to the four parts on the upstream side of the fins 6 through the hole 1 (). 1.j additional vanes 17 are provided at the bottom of the flow F fill for feeding engine oil. - Due to the above structure, even if the sealing device 6 stops functioning due to a temporary decrease in the engine oil level, the engine oil level will be removed from the fins as soon as the engine oil supply is opened. It is possible to reliably restore the function of the seal≠16 by putting it in the flow Wi11 and maximizing the pressure due to centrifugal force.

[Brief explanation of the drawing]

FIG. 1 shows a pair of 11
FIG. 2 is a t-plane sectional view of a pair of shafts including another 7-wheel device according to the present invention. 1.2...shaft, 3...recess, 4...upstream weir,
5... Downstream side 1 匪, 6... Fin, 7... Liquid supply device, 8... Hole, 9... ++5 cylinder, lO...
・Pump's farthest end wall on the 6+U side, 12... Annular path, 13... Gap, [5... Side plate, 16... Hole, 1
7...Blade, A...Direction of gas flow. Applicant's agent Inomata Kiyoshi Procedural amendment (method) 1. Indication of the case Showa era q-h-h'1° Application No. 142367 2. Name of the invention Hydraulic seal device 3. Person making the amendment Case and Relationship between Patent application population - Rousseau Royce, Limited 12

Claims (1)

[Claims] 1. Between two components that undergo relative rotational movement;
A recess formed between the upstream weir and the downstream weir of the component having a higher rotational speed among the components and radially inward; a device for supplying liquid to the recess; a sealing member provided on the other component and protruding into the four parts to the extent that it is sufficiently immersed in the liquid held in the four parts by the action of centrifugal force; It rotates together with the components on the side, takes in liquid from the liquid supply device or the upper part, drives this liquid sufficiently to the speed of the components, and transfers the driven liquid to the four parts. A hydraulic seal device comprising: a pump disposed so as to discharge from one pupil and one east end in a radial direction. 2. The above-mentioned 218 cylinder is installed on a wall extending radially inward of the high-speed side component.
Claims: A hydraulic seal device having r4T characteristics. 3. There is a wall extending in the radial direction at a distance from this tank on the downstream side of the above-mentioned speed side components, and there is a wall extending in the radial direction with a distance between the -L wall and the above weir. A hydraulic seal device according to claim A'iJ2, characterized in that the blade is sharpened in between. 4. An annular path is formed between the radially outer end of the downstream weir and the radially inner surface of the component, and the liquid discharged by the pump described in I.2 is passed through this annular path. l
A hydraulic seal device according to claim 3. 5. The wall body extending inward in the radial direction extends inwardly more widely than the weir of the Dingryuwei.
Hydraulic seal family 14 according to claim 4. 6. A wall in which a cylindrical plate surrounds the high-speed component at a radial distance and terminates at the F flow side end of the radially inwardly extending wall; the body extends inward 11111 to a narrower extent than said downstream weir, - a device for supplying liquid into said recess is arranged to cause said liquid to flow into the radially inner end of said vane; The blades have a structure such that the blades transport the liquid 70 times from the liquid supply device into the space between the side plate and the components, and also have one or more blades in the components. The hydraulic seal according to claim 3, characterized in that it has a structure in which two or more holes are provided, and the liquid flows through the holes to the outermost part in the radial direction of the recess during operation. Device. 7. The hydraulic sealing device according to claim 86, wherein the hole that does not penetrate the component is provided on the upstream side of the sealing member. 8. The hydraulic pressure according to any one of the above-mentioned items 1J4-1 of the claims, characterized in that the components that make relative rotational movements are two shafts that make relative rotational movements of a gas turbine engine. Seal device needle for. 9. The hydraulic seal device according to claim 8, wherein the two shafts rotate in opposite directions.