KR101950924B1 - complex sealing apparatus for turbine - Google Patents

Abstract

Provided in the present invention is a composite sealing apparatus for a turbine, which is mounted on the inner circumferential surface of a fixating body opposed to an end part of a blade of a rotary body, in order to seal the flow of fluid flowing between the fixating body and the rotary body of a turbine, thereby improving sealing performance with respect to the fluid flowing between the fixating body and the rotary body. To this end, the composite sealing apparatus for a turbine comprises: a first guardian chamber; a first honeycomb chamber; a brush chamber; a second honeycomb chamber; and a second guardian chamber.

Description

Complex sealing apparatus for turbine

The present invention relates to a composite sealing device for a turbine, and more particularly, to a composite sealing device for a turbine that improves sealing performance for fluids flowing between a stationary body and a rotating body.

Generally, a turbine is a machine that converts the energy of a fluid such as water, gas or steam into rotational force. That is, a turbo type machine in which a rotary body formed with blades along the outer periphery is rotatably disposed inside a casing, and high-temperature steam or gas is blown to the blades to rotate at a high speed.

In this turbine, the fluid leaking between the rotating body and the fixed casing is a main cause of increasing the fuel cost by lowering the efficiency of the turbine, so that the importance of the design technique of the sealing device for reducing the fluid leakage is increasing, And it plays an important role in reducing vibration generation of the rotating body due to abnormal behavior of the fluid.

FIG. 1 is a cross-sectional view showing a state in which a conventional honeycomb-type sealing apparatus is mounted on a turbine, and FIG. 2 is a sectional view showing a conventional honeycomb-type sealing apparatus.

1 to 2, a conventional honeycomb-type sealing apparatus 5 is installed in an outer ring and an inner ring of a diaphragm 3 mounted on a casing 2. [ The honeycomb type sealing device 5 is a non-contact type sealing device that reduces the leakage flow rate by using a throttling process of fluid passing through the honeycomb groove 6.

In detail, the fluid passes along the space between the honeycomb groove 6 and the rotating body 1, which are arranged in sequence along the fluid flow direction. By the pressure drop effect generated in the process of repeating throttling and expansion, Can be reduced.

However, the labyrinth-type sealing device 5 has to have a larger number of the honeycomb holes 6 in order to increase the pressure drop efficiency. In addition, although the pressure reducing effect is increased in the above case, there is a problem that vibration of the rotating body 1 is caused as the leakage flow rate is rapidly reduced. In addition, there is a problem that loss of rotational force occurs due to vibration of the rotating body 1, and efficiency of the turbine is lowered.

3 is a cross-sectional view of a conventional brush sealing apparatus.

3, the conventional brush sealing apparatus includes a brush portion 7 for sealing the gap between the rotary body 1 and the diaphragm 3, and a brush portion 7 for covering and supporting the front and rear sides of the brush portion 7 And a bristle plate (8, 9).

Here, the brush part 7 has a plurality of densely packed bristles, and divides the high-pressure area and the low-pressure area to reduce the flow of the leaked fluid.

At this time, since each of the bristles contacts the rotor portion 1 with the lower end portion sealed in the state where the upper end portion is fixed, the leakage of the fluid can be somewhat reduced as compared with the labyrinth type sealing device by sealing the fluid, So that the amount of rotational motion loss is reduced as the outer periphery of the rotor portion 1 is supported.

However, due to vibration during rotation of the rotor, the bristles wear differently in each portion of the brush, thereby increasing the amount of leakage of fluid through the worn-out portion. In addition, the concentration of the leakage fluid and the biased There is a problem that the amount of vibration of the rotor portion is increased due to deterioration. In addition, since the fluid passing through the brush sealing device flows to the brush without energy loss due to the inflow and repetition, there is a problem that abrasion of the bristle rapidly proceeds.

Korea Patent No. 10-0541592

SUMMARY OF THE INVENTION In order to solve the above problems, the present invention provides a hybrid sealing device for a turbine having improved sealing performance against fluid flowing between a stationary body and a rotating body.

In order to solve the above problems, the present invention provides a turbine composite sealing device mounted on an inner circumferential surface of the fixture so as to face a blade end of the rotator so as to seal a flow of fluid flowing between a fixture of the turbine and the rotator Wherein the fluid is disposed in the inflow direction of the fluid so that the fluid undergoes reduced pressure through the throttling action, the fluid being disposed at a predetermined first interval between the radially inner end and the outer periphery of the rotating body, 1 Guardian room; And a second guardian seal disposed between the first guardian chamber and the outer circumference of the rotating body, And a plurality of first radially outwardly recessed first and second radially outwardly protruding radially outwardly facing radially inner surfaces of the first and second radially outwardly facing first and second radially outward surfaces of the rotating body so as to surround the rotating body at predetermined second intervals exceeding the first spacing, A first honeycomb chamber on which a honeycomb is formed; Arranged so as to surround the rotating body at a predetermined third interval between the radially inner end and the outer periphery of the rotating body so that the reduced fluid flows under reduced pressure; and a second honeycomb filter A brush room including a bristle; A plurality of second honeycomb grooves are formed to surround the rotating body at the second gap, the plurality of second honeycomb grooves being recessed radially outward along the inner circumferential surface opposed to the rotating body, A second honeycomb chamber; And a second honeycomb filter disposed in the second honeycomb chamber in a direction in which the fluid advances, the rotating body being enclosed at the first interval so as to restrict eccentric rotation of the rotating body due to a pressure deviation of the fluid, Wherein the first guardian chamber and the second guardian chamber comprise a plurality of flow slit holes penetrating in the axial direction so as to increase the flow area of the fluid, And a crown support portion branched by the slit hole, wherein the crown support portion is provided such that the circumferential width decreases toward the radially inward side so as to reduce the friction area with respect to the outer circumference of the rotary body, And the fluidized slit hole is formed so as to have a circumferential width in the radially inward direction so that the fluid is concentrated on the outer circumferential side of the rotating body Wherein the first and second turbine blades are mounted on the turbine shaft.

Wherein the third gap is set to be less than the first gap so that the radially inner end of the brush seal is located adjacent to the rotator than the radially inner end of the first guardian seal, desirable.

A first gap distance between the first and second honeycomb chambers and between the second honeycomb chamber and the second guardian chamber is set to a predetermined distance in the axial direction so that the fluid is diffused and reduced to the entire area of the flow area. Wherein a radial distance between the first guardian chamber and the first honeycomb chamber and between the flat surface formed between the second honeycomb chamber and the second guardian chamber and the outer periphery of the rotating body is the second gap And a fourth diaphragm portion and a fourth diaphragm portion that are set at a fourth interval exceeding the first diaphragm portion and the fourth diaphragm portion, respectively.

The first honeycomb chamber and the second honeycomb chamber are spaced apart from each other by a predetermined distance in the axial direction so that the fluid is diffused and decelerated between the first honeycomb chamber and the brush chamber and between the brush chamber and the second honeycomb chamber, It is preferable that a second throttling portion and a third throttling portion are formed between the brush room and the flat surface respectively formed between the brush room and the second honeycomb chamber and the outer periphery of the rotating body, Do.

delete

Through the above-mentioned solution, the present invention provides the following effects.

First, the radial and axial fluid flow is controlled by the combination and arrangement sequence of each honeycomb chamber, each guardian chamber, and brush chamber forming a turbulent stagnation layer to seal the fluid flow flowing between the fixture and the rotating body of the turbine The sealing performance of the device and the rotating efficiency of the rotating body can be remarkably improved.

Secondly, since a plurality of throttling portions spaced apart from each other are formed so as to be spread and decelerated over the entire area of the flow area when the fluid flows at intervals between the respective guardian chambers, honeycomb chambers, and brush chambers, The sealing efficiency and performance of the device can be remarkably improved.

Third, the radial distance of each of the shunting portions is set to a fourth gap exceeding a second gap, which is a gap between the honeycomb chambers and the outer periphery of the rotating body, and the axial gap is set to a first gap distance and a second gap distance The flow-in fluid is diffused and stagnated to each of the throttle portions, so that the kinetic energy of the fluid is consumed and the sealing efficiency can be improved.

Fourth, the radially inner end of the brush seal is positioned adjacent to the radial inner end of the first guardian seal and the second guardian seal, thereby narrowing the gap between the bristles and the rotating body to increase the shielding area, Can be improved.

1 is a cross-sectional view showing a state in which a conventional honeycomb-type sealing apparatus is mounted on a turbine.
2 is a side sectional view showing a conventional honeycomb-type sealing apparatus.
3 is a side cross-sectional view of a conventional brush seal device;
4 is a cross-sectional view illustrating a state in which a hybrid sealing apparatus for a turbine according to an embodiment of the present invention is mounted on a turbine.
5 is a side cross-sectional view of a composite sealing apparatus for a turbine according to an embodiment of the present invention.
6 is a cross-sectional exemplary view showing a second honeycomb groove of a turbine composite sealing apparatus according to an embodiment of the present invention.
FIG. 7 is a front view of a Guardian chamber of a composite sealing apparatus for a turbine according to an embodiment of the present invention. FIG.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a hybrid sealing apparatus for a turbine according to a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

FIG. 4 is a cross-sectional view showing a state in which a hybrid sealing apparatus for a turbine according to an embodiment of the present invention is mounted on a turbine, FIG. 5 is a side sectional view showing a composite sealing apparatus for a turbine according to an embodiment of the present invention, 6 is a cross-sectional view illustrating a second honeycomb groove of a turbine composite sealing apparatus according to an embodiment of the present invention, and FIG. 7 is a front view illustrating a Guardian chamber of a turbine composite sealing apparatus according to an embodiment of the present invention .

4, the hybrid sealing apparatus 100 for a turbine according to an embodiment of the present invention includes a turbine housing 20 and a rotating body 10, And can be mounted on the inner peripheral surface of the fixture 20.

4, the fluid f introduced into the turbine passes through the casing, the diaphragm fixed to the inside of the casing, the partition 27, and the like to rotate the blade 27a of the rotor portion. The fluid f is discharged to the outside through the step of rotating the next blade in accordance with the guidance of the partition 27 and the power generation process of converting the rotational force into electrical energy is transmitted to the power generation device .

Here, the rotating body 10 is a portion rotated by a fluid f, such as steam, which flows into the turbine, and includes a rotor portion, which is a shaft connected to the external power generation device and transmits rotational force, And a blade 27a for forming a rotational force.

The fixed body 20 preferably includes a casing defining a space defined from the outside to allow steam to flow therein and a diaphragm or partition 27 for controlling the flow direction or path of the steam Do. The inner circumferential surface of the fixture 20 is preferably a radially inner cross section of the casing, the diaphragm, the partition 27 or the like facing the blade 27a or the rotor portion.

Here, the composite sealing apparatus 100 for a turbine is provided in a ring shape and is arranged to cover an annular space between a radially outer end of the rotating body 10 and a radially inner end of the fixture 20. The turbine composite sealing apparatus 100 may be arranged in multiple stages in the axial direction by providing a plurality of the turbine compound sealing apparatuses 100 in accordance with the axial length and area of the annular space, the fluid pressure, and the like. The term sealing the flow of the fluid f means that the high pressure region on the inflow direction of the fluid and the low pressure region on the inflow direction side of the fluid on the basis of the blade of the rotating body 10, It is preferable to understand that it means to reduce the pressure of the fluid in the high pressure region and then to flow into the low pressure region. Of course, the hybrid sealing apparatus 100 for a turbine may be constructed in such a manner that the sealing between the fixed body 20 and the rotating body, such as between the casing and the end of the blade 27a, between the casing and the cylindrical body portion of the rotor, So that the leakage flow of the fluid to the place can be reduced.

5 to 7, the turbine composite sealing apparatus includes a first guardian chamber 120, a first honeycomb chamber 130, a brush chamber 140, a second honeycomb chamber 150, And a seal 160. Here, the first guardian chamber 120, the first honeycomb chamber 130, the brush chamber 140, the second honeycomb chamber 150, and the second guardian chamber 160 are connected to the fixed body 20, but it may be integrally provided in the fixing member 20 in a state where the sealing member 110 is installed on the sealing member 110 for ease of mounting and maintenance. At this time, the sealing portion 110, the first guardian chamber 120, the first honeycomb chamber 130, the brush chamber 140, the second honeycomb chamber 150, the second guardian chamber 160 ) Or its components are preferably provided as ring-shaped members, and are more preferably divided into circular arcs of a predetermined angle for easy mounting and maintenance, so as to form a complete ring when connected in the circumferential direction.

The ring-like member is preferably manufactured by centrifugal casting and is preferably divided at a predetermined angle, and each member can be accurately manufactured to match the inner shape of the fixing member 20 or the sealing member 110, The radially inner ends of the members provided in the sealing portion 110 can be precisely manufactured and arranged such that the spacing is uniformly formed in the circumferential direction at a predetermined interval from the outer periphery of the rotating body 10. [

The sealing portion 110 is formed in a region between the inner periphery of the fixing body 20 and the outer periphery of the rotating body 10 disposed at the center of the fixing body 20, Shaped member corresponding to the inner circumferential surface of the fixing member 20, and the outer end thereof is engaged with the inner circumference of the fixing member 20. [ At this time, the sealing portion 110 is divided into two or more arcuate shapes and each divided end portion is sequentially joined to the inner periphery of the fixing body 20, so that the sealing portion 110 is disposed so as to completely cover the outer diameter of the rotating body 10 .

A plurality of bolt fastening holes may be formed at predetermined intervals along the circumferential direction of the fixing body 20 at both ends of the sealing portion 110 in the axial direction. Here, the bolt fastening hole may have a stepped shape corresponding to the shape of a fastening bolt (k) formed with a head portion protruding outward at an upper end portion. Accordingly, as the fastening bolt (k) is inserted and fastened to the bolt fastening hole, the sealing part 110 and the fixing body 20 can be coupled to each other.

As a matter of course, a predetermined annular space portion may be formed between the radially inward end of the sealing portion 110 and the rotating body 10. For this, an engaging groove (not shown) may be formed along the circumferential direction on the inner circumference of the fixing body 20, and a radial outer end of the sealing portion 110 may be provided with an engaging groove (Not shown) may be formed. In addition, the engaging groove (not shown) and the engaging projection (not shown) may be formed in a dovetail shape in the circumferential direction, and may be slidably engaged in the circumferential direction and prevented from being radially inwardly separated. At this time, an elastic member (not shown) such as a leaf spring may be provided between the coupling groove (not shown) and the coupling protrusion (not shown), and the sealing portion 110 may be provided on the elastic member And can be elastically supported radially inward.

That is, the first guardian chamber 120 and the second guardian chamber 160 provided in the sealing portion 110 are maintained in a state of being adjacent to the rotary body 10 by a pressing force of the elastic member (not shown) When the rotating body 10 is in contact with the first and second guardian chambers 120 and 160 due to vibration and expansion and applies a force greater than the elastic force of the elastic member (not shown) (110) can be moved radially outward. Accordingly, it is possible to prevent the first guardian chamber 120 and the second guardian chamber 160 from being excessively brought into contact with the surface of the rotating body 10 rotated at a high speed, 120 and the second guardian chamber 160 are reduced and the rotational loss of the rotating body 10 due to the contact friction between the first guardian chamber 120 and the second guardian chamber 160 is reduced .

The sealing part 110 may be formed in the first guardian chamber 120, the first honeycomb chamber 130, the brush chamber 140, the second honeycomb chamber 150, the second guardian chamber 160 It is preferable to extend in the axial direction in consideration of respective axial thicknesses and installation intervals. At this time, it is preferable that the sealing part 110 is made of a metal material such as stainless steel having high strength and corrosion resistance, and strength reduction and corrosion due to contact with the fluid can be minimized while stably supporting the installed members .

The first guardian chamber 120 is disposed in the inflow direction of the fluid f so that the fluid f undergoes reduced pressure through the throttling action and is disposed between the radially inner end portion and the outer periphery of the rotating body 10 The first gap A may be spaced apart from the first gap A so as to surround the rotating body 10.

In detail, the first guardian chamber 120 is disposed at the front end of the sealing portion 110 in the inflow direction of the fluid f. At this time, the first guardian chamber 120 may be integrally formed at the front end of the sealing portion 110, or may be formed as a separate member. That is, the first guardian chamber 120 is mounted on the sealing portion 110 and disposed in the circumferential direction along the annular space portion formed between the radially inward end of the sealing portion 110 and the rotating body 10 .

Here, when the first guardian room 120, the brush room 140, and the second guardian room 160 are provided as separate members and are coupled to the sealing part 110, the sealing part 110 (Not shown) on which the first guardian chamber 120 is mounted, a second mounting groove 115 on which the brush chamber 140 is mounted, and a second mounting groove 115 on which the second guardian chamber 160 is mounted A third mounting groove (not shown) may be formed. In this case, each of the mounting grooves is formed to be recessed toward the outside in the radial direction, and is extended in the circumferential direction so as to correspond to the respective chambers (130, 140, 150) installed in the chambers and is extended from the front end portion of the sealing portion The first mounting groove (not shown), the second mounting groove 115, and the third mounting groove (not shown) may be sequentially formed. At this time, the mounting grooves may be spaced apart from each other by a predetermined distance in the axial direction. In some cases, a labyrinth seal may be provided on the inner circumferential surface of the sealing portion 110 corresponding to each of the mounting grooves.

Preferably, the first guardian chamber 120 is provided to surround the rotating body 10 at the predetermined first interval A. That is, the first guardian chamber 120 is spaced from the radially inward end of the first guardian chamber 120 through the sealing portion 110 to the outer periphery of the rotating body 10, It is preferable that the radial size is set so as to satisfy the following equation (A).

The first guardian chamber 120 is disposed adjacently to the outer circumference of the rotating body 10 so as to support the rotating body 10 in contact with the outer circumference of the rotating body 10 when the rotating body 10 vibrates or eccentrically rotates And the loss of the rotational force can be reduced by restricting the vibration or the eccentric rotation of the rotating body 10. That is, the eccentricity or vibration range of the rotating body 10 may be limited to within the first gap A by the first guardian chamber 120, And can be automatically adjusted as it is supported radially inward by the seal 120.

Preferably, the first guardian chamber 120 is formed of a material having a hardness lower than that of the material forming the rotary body 10, and has a low coefficient of friction, , Copper or a copper alloy nickel alloy, or the like.

Accordingly, when the first guardian chamber 120 is contacted with the rotating body 10, the rotating body 10, which is an expensive precision component, can be safely protected, and the rotating body 10 can be safely protected with a low friction coefficient. The loss of rotational force can be reduced.

The first honeycomb chamber 130 is disposed in the advancing direction of the fluid f from the first guardian chamber 120 and between the radially inner end portion and the outer periphery of the rotating body 10, The first fluid passage is provided to surround the rotating body at a predetermined second interval B exceeding the predetermined value A, and the fluid (f), which is depressurized when passing through the first guardian chamber (120) A plurality of first honeycombs 130a recessed radially outward along the inner circumferential surface opposed to the entire body 10 are formed.

That is, the first honeycomb chamber 130 is mounted to the sealing portion 110 so as to be positioned rearward from the first guardian chamber 120, and the radial inward end of the sealing portion 110 and the inner end of the rotating body 10 In the circumferential direction. Here, the first honeycomb 130 may be integrally formed on the inner circumferential surface of the sealing portion 110, or may be formed of a separate member.

The first honeycomb chamber 130 is provided to surround the rotating body 10 at a predetermined second interval B exceeding the first interval A. That is, it is preferable that the radial size of the first honeycomb compartment 130 is set so that the interval between the radially inward end and the outer circumference of the rotating body 10 forms the second interval B. In this case, the second interval B may be set to a predetermined interval exceeding the first interval A. That is, the radially inner end of the first honeycomb chamber 130 is located radially outward of the radial inner end of the first guardian chamber 120.

The first honeycomb 130a has a first honeycomb 130a having a polygonal cross-section formed by an inner circumferential surface opposed to the rotating body 10, that is, a hexagonal cross-section that is recessed radially outward at the radially inner end, Are formed at a plurality of locations. In detail, the fluid f passing through the first guardian part 120 is reduced in pressure by a predetermined amount and passed between the first honeycomb chamber 130 and the rotating body 10.

Here, the fluid flowing along the outer circumference of the rotating body 10 is sucked into the inner space of the first honeycomb groove 130a, and is guided to be circulated and discharged along the inner surface. That is, the inlet fluid of the first honeycomb 130a is circulated along the inner wall of the groove, a part thereof is discharged to the rotating body 10 side, and a part thereof is recirculated along the inner wall of the groove and flows along the rotating body 10 A turbulent stagnation layer is formed that reduces the flow rate of the fluid and interferes with the flow of the fluid f along a plurality of axially and circumferentially arranged first honeycomb holes 130a. At this time, a substantial barrier layer may be formed which decelerates the fluid (f) by interrupting the flow of the fluid (f) flowing in the subsequent flow in the axial direction of the fluid (f) discharged from the first honeycomb .

At this time, the fluid depressurized through the first guardian chamber 120 flows between the inlet of the first honeycomb groove 130a and the rotating body 10, so that the radial outward deep portion of the first honeycomb groove 130a And the entire area of the wall surface in the first honeycomb 130a can be utilized as the circulation region of the fluid. Accordingly, even when the first honeycomb chamber 130 having the same area and depth is used, the circulation path of the fluid can be increased, and the efficiency of deceleration / decompression due to the circulation of the fluid can be maximized, Can be remarkably improved.

The turbulent stagnation layer may form a predetermined deviation pressure region along the outer circumference of the rotating body 10 to cause the rotating body 10 to vibrate or eccentrically flow. At this time, since the eccentric flow of the rotary body 10 is limited through the first guardian chamber 120 on the front side of the first honeycomb chamber 130, the rotational loss of the rotary body 10 can be reduced . In addition, the first honeycomb chamber 130 is spaced apart from the rotating body 10 by the second gap B, and when the rotating body 10 vibrates or rotates, the first guardian chamber 120 Is first brought into contact with the rotating body (10). Accordingly, direct contact friction between the first honeycomb 130 and the rotating body 10 can be prevented, and the durability of the apparatus can be improved.

The brush chamber 140 is disposed in the advancing direction of the fluid f from the first honeycomb chamber 120 and has a radially inner end and an outer periphery of the rotatable body 10 so that the reduced fluid flows under reduced pressure, And a plurality of bristles 141 arranged to surround the rotating body 10 at a predetermined third interval C between the bristles 141.

In detail, the brush chamber 140 is disposed in a direction in which the fluid f advances from the first honeycomb chamber 130. That is, the brush chamber 140 is mounted to the second mounting groove 115 of the sealing portion 110 so as to be positioned rearward from the first honeycomb chamber 130, And may be arranged in a circumferential direction along an annular space portion formed between the inner end and the rotating body 10. [ Of course, the brush chamber 140 may be integrally formed with the sealing portion 110, as the case may be.

The brush chamber 140 may include a plurality of brushes 140 arranged to surround the rotating body 10 at predetermined third intervals C exceeding the first interval A and the second interval B, And the bristles 141. The bristles 141 are made of a flexible material having elasticity and heat resistance and are formed so as to be densely packed with adjacent bristles so that the radially outer ends of the bristles 141 may be formed of a gas tungsten arc welding (GTAW) Arc Welding (PAW), or a high-temperature stable adhesive material to form the brush seal 140.

Here, the radially outer end of the bristles 141 may be directly fixed to the second mounting groove 115. However, in order to facilitate mounting and maintenance, And is integrally provided in the second mounting groove 115. At this time, when the radially outer end of the bristles 141 is mounted to the second mounting groove 115 through the casing 142, the gap between the radially inner end and the outer circumference of the rotating body 10 And the radial length is set so as to form the third gap (C).

The casing 142 is provided with a shock preventing portion 142a for covering the front of the bristles 141 and a supporting portion 142b for supporting the rear of the bristles 141, Thereby reducing the amount of deformation of the bristles 141 due to the elasticity of the bristles 141. The gap between the radially inner end of the shock preventing portion 142a and the support portion 142b and the outer circumference of the rotating body 10 preferably exceeds the third gap C. [

Specifically, the fluid (f), which has flowed axially through the first guardian chamber (120) and the first honeycomb chamber (130), passes through the radially inner end side of the brush chamber (140) . The front side fluid f of the brush chamber 140 flows into the dense space between the bristles 141 through the space between the shock preventing portion 142a and the rotating body 10, Through the space between the supporting portion 142b and the rotating body 10, as shown in FIG. In this process, the fluid (f) can be depressurized.

Here, the bristles 141 increase the supporting force against the bending in the forward and backward direction through the shock preventing portion 142a and the supporting portion 142b, but may not be enough to support the circumferential bending. At this time, since the fluid f passing through the brush chamber 140 is in the state of being decelerated in the axial direction by the first guardian chamber 120, the first honeycomb chamber 130 and a second throttling portion Circumferential deformation of the bristles 141 not supported by the casing 142 can be minimized. Accordingly, the reduced pressure of the fluid (f) passing through the brush chamber (140) can be increased to improve the sealing performance of the apparatus.

The bristles 141 constituting the brush chamber 140 are spaced apart from the rotating body 10 by the third gap C, That is, the radially inner end of the brush chamber 140 is positioned radially inward from the radially inner end of the first guardian chamber 120. Accordingly, when the rotary body 10 is eccentrically rotated, the bristles 141 first come into contact with the rotary body 10 more than the first guardian chamber 120.

The radially inner end of the brush chamber 140 is located adjacent to the radially inner end of the first guardian chamber 120 and the second guardian chamber 160 adjacent to the rotator 10, The sealing performance of the device can be improved since the space between the bristles 141 and the rotating body 10 is narrowed to increase the shielding area.

In addition, the fluid (f) decelerated through the first guardian chamber (120), the first honeycomb chamber (130), and the second throttle portion flows into the brush chamber (140) 140) is minimized while the deterioration of the sealing performance is minimized, so that the sealing performance of the device can be improved and maintained for a long period of time.

The second honeycomb chamber 150 is disposed in the direction of advance of the fluid f from the brush chamber 140 so as to surround the rotating body 10 at the second gap B, A plurality of second honeycombs 150a recessed radially outward along the inner circumferential surface opposed to the rotating body 10 are formed.

In detail, the second honeycomb chamber 150 is disposed in the advancing direction of the fluid f from the brush chamber 140. That is, the second honeycomb chamber 150 is mounted on the rear end of the sealing portion 110 so as to be positioned rearward from the brush chamber 140, and the radial inward end of the sealing portion 110 and the rotating body 10 in the circumferential direction. At this time, the second honeycomb 150 may be integrally formed on the inner circumferential surface of the sealing part 110, or may be formed as a separate member.

The second honeycomb chamber 150 is provided to surround the rotating body 10 at the second interval B. That is, in the state where the radially outer end of the second honeycomb chamber 150 is mounted on the sealing portion 110, the distance between the radially inward end and the outer circumference of the rotating body 10 is smaller than the second spacing B It is preferable that the radial length is set.

At this time, the second honeycomb compartment 150 is provided with the second honeycomb groove 150a having a polygonal cross-section formed by an inner circumferential surface opposed to the rotating body 10, that is, a hexagonal cross section that is recessed radially outward along the radially inward end, . Specifically, the fluid f through the brush chamber 140 is reduced in pressure by a predetermined amount, decelerated at a third throttling portion to be described later, and passed between the second honeycomb chamber 150 and the rotating body 10.

The second honeycomb 150a sucks the fluid f flowing along the outer circumference of the rotating body 10 into the inner space and induces the circulation and discharge of the fluid f along the inner surface. In other words, the fluid (f) at the inlet side of the second honeycomb groove 150a is circulated along the inner wall of the groove, a part thereof is discharged to the rotating body 10 side, a part is recirculated along the inner wall of the groove, A turbulent stagnation layer is formed which interferes with the flow of the fluid f along the plurality of axially and circumferentially arranged openings of the second honeycomb 150a, reducing the flow rate of the flowing fluid f .

At this time, since the fluid f reduced through the brush chamber 140 flows between the inlet of the second honeycomb groove 150a and the rotating body 10, the radial outside of the second honeycomb groove 150a And the whole area of the wall surface in the second honeycomb groove 150a can be utilized as a circulation region of the fluid f. Accordingly, even when the second honeycomb chamber 150 having the same area and depth is used, the circulation path of the fluid f can be increased and the efficiency of deceleration / decompression due to the circulation of the fluid f can be maximized So that the efficiency of the apparatus and the sealing performance can be remarkably improved.

On the other hand, the turbulent stagnation layer may form a predetermined deviation pressure region along the outer circumference of the rotating body 10 to cause vibration or eccentric flow of the rotating body 10. At this time, since the eccentric flow of the rotary body 10 is restricted through the second guardian chamber 160 on the rear side of the second honeycomb chamber 150, the rotational force loss of the rotary body 10 can be reduced. In addition, the second honeycomb chamber 150 is spaced apart from the rotating body 10 by the second gap B, and when the rotating body 10 vibrates or rotates, the second guardian chamber 160 Is first brought into contact with the rotating body (10). Through this, direct contact friction between the second honeycomb chamber 150 and the rotating body 10 can be prevented, and the durability of the apparatus can be improved.

The second guardian chamber 160 is disposed in the second honeycomb chamber 150 in the direction in which the fluid f advances and the eccentricity of the rotating body 10 due to the pressure- And is made of a low-hardness material having a hardness less than a hardness of the rotating body 10, the rotating body 10 being wrapped around the first gap A so that rotation is restricted.

In detail, the second guardian chamber 160 is disposed in a direction in which the fluid f advances from the second honeycomb chamber 150. That is, the second guardian chamber 160 is provided integrally with the sealing portion 110 so as to be positioned rearward from the brush chamber 140, so that the radial inward end of the sealing portion 110, And is disposed in the circumferential direction along the annular space portion formed between them. Of course, the second guardian chamber 160 may be mounted on the third mounting groove (not shown) as the case may be.

The second guardian chamber 160 is provided to surround the rotating body 10 at the first interval A. That is, it is preferable that the second guardian chamber 160 is set to have a radial size such that the interval between the radially inward end and the outer circumference of the rotating body 10 forms the first interval A. That is, the radially inner end of the brush chamber 140 is disposed adjacent to the outer periphery of the rotator 10 than the radially inner end of the second guardian chamber 160.

In detail, the fluid passing through the brush chamber 140 flows along a narrow gap between the bristles 141 and is depressurized, and a pressure deviation due to a reduced pressure between the fluid in front of and behind the brush chamber 140, That is, a decompression deviation occurs. At this time, the front fluid and the rear fluid of the brush chamber 140 press the outer circumference of the rotating body 10 with a different elevation pressure, and eccentric rotation may be generated due to tilting of the rotating body 10 .

The second guardian chamber 160 is disposed adjacently to the outer circumference of the rotating body 10 so that the second guardian chamber 160 contacts the outer circumference of the rotating body 10 when the rotating body 10 is tilted or eccentrically rotated, And it is possible to reduce the loss of rotational force by restricting the vibration or eccentric rotation of the rotating body 10. That is, the eccentricity or vibration range of the rotary body 10 may be limited to within the first interval A by the second guardian chamber 160, and the rotary body 10 may have an outer circumference at the time of eccentricity, Can be automatically adjusted as it is radially inwardly supported by the two guardian chambers (160). At this time, the second guardian chamber 160 is made of a low-hardness brass, copper alloy or nickel alloy, so that the second guardian chamber 160 is worn more precisely than the rotatable body 10, .

The fluid (f) flows between the first guardian chamber (120) and the first honeycomb chamber (130) and between the second honeycomb chamber (150) and the second guardian chamber (D) in which a radial distance is set to a fourth spacing (D) that is set to a predetermined first spacing distance (E) And a fourth throttle portion are respectively formed.

In detail, the first throttle portion and the fourth throttle portion are disposed between the first guardian chamber 120 and the first honeycomb chamber 130 and between the second honeycomb chamber 150 and the second guardian chamber 160 And a first gap distance E between the first guardian chamber 120 and the first honeycomb chamber 130 is set to a predetermined distance in the axial direction so that the fluid f is diffused and reduced across the entire flow area, And a radial distance between the flat surface formed between the second honeycomb chamber (150) and the second guardian chamber (160) and the outer circumference of the rotating body is greater than the second gap (B) It is preferable to set it to the fourth interval (D).

It is preferable that the first throttle portion is an empty space in which the axial gap between the first guardian chamber 120 and the first honeycomb chamber 130 is formed at the first separation distance E. [ That is, the first separation distance E is preferably an interval between the first guardian chamber 120 and the first honeycomb chamber 130. It is preferable that the first throttle portion is an annular space formed between the first guardian chamber 120 and the first honeycomb chamber 130.

Preferably, a flat surface located radially outward of the second gap B is formed in the first throttle portion. Here, it is preferable that a radial length of the first throttle portion is set so that the interval between the outer circumference of the rotating body 10 and the flat surface exceeds the second interval B. That is, it is preferable that the interval between the flat surface and the outer circumference of the rotating body 10 is set to a fourth interval (D) exceeding the second interval (B). At this time, it is more preferable that the flat surface is formed in a ring shape and is divided into a circular arc of a predetermined angle so as to form a complete ring shape when connected in the circumferential direction. It is preferable that such a flat surface is produced by centrifugal casting in the form of a ring and divided at a predetermined angle. That is, the flat surface is preferably one side of the sealing part 110 formed between the first guardian chamber 120 and the first honeycomb chamber 130 at the first spacing distance E .

Here, the fluid (f) throttled by the throttling action at the first gap (A) between the first guardian chamber (120) and the rotating body (10) Expanding and decelerating in a wide space between the entire bodies 10, and forming a predetermined expansion pressure in the adjacent region at the time of expansion. At this time, the inflation pressure is increased in proportion to the deviation between the flat surface and the rotating body 10 and the gap between the rotors 10 from the inner circumference of the sealing portion 110, It forms a large pressure. Further, the fluid (f) advancing from the first throttle portion may flow into the first honeycomb chamber (130).

The fourth gap (E) is set between the second honeycomb chamber (150) and the second guardian chamber (160) so that the fluid (f) A shaft portion is formed. In this case, the fourth throttle portion is preferably the same as the first throttle portion, and a detailed description thereof will be omitted.

Here, the fluid f passing through the turbulent stagnation layer of the second honeycomb chamber 150 is expanded and decelerated in a wide space between the flat surface of the fourth throttle portion and the rotating body 10, A predetermined expansion pressure is formed in the adjacent region when inflated. At this time, the inflation pressure is increased in proportion to the deviation between the flat surface and the rotating body 10 and the gap between the rotors 10 from the inner circumference of the sealing portion 110, It forms a large pressure. In addition, the fluid f may pass through the second guardian chamber 160 and may be depressurized by the diaphragm action and flow backward of the sealing portion 110.

Accordingly, a plurality of throttling portions are provided so as to be spread and decelerated to the entire area of the flow area during the flow of the fluid f at intervals between the guardian chambers 120, 160, the honeycomb chambers 130, 150 and the brush chamber 140 As the deceleration and decompression of the fluid are repeated, the kinetic energy of the fluid is rapidly reduced, so that the sealing efficiency and performance of the device can be remarkably improved.

An axial gap is formed between the first honeycomb chamber 130 and the brush chamber 140 and between the brush chamber 140 and the second honeycomb chamber 150 so that the fluid f is diffused and decelerated. A second throttling portion and a third throttling portion in which a radial gap is set to the fourth gap D are formed.

In detail, the second throttling portion and the third throttling portion are disposed between the first honeycomb chamber 130 and the brush chamber 140 and between the brush chamber 140 and the second honeycomb chamber 150, the first honeycomb chamber 130 and the brush chamber 140 and the brush chamber 140 and the second honeycomb chamber 130 are spaced apart from each other by a predetermined distance G, And the radial distance between the flat surface formed between the second honeycomb chambers 150 and the outer circumference of the rotating body is set to the fourth gap D. [

Preferably, a flat surface positioned radially outward of the second gap B is formed in the second shaft portion and the third shaft portion. Here, it is preferable that the radial length of the second throttle portion and the third throttle portion is set so that the interval between the outer circumference of the rotating body 10 and the flat surface exceeds the second interval B. That is, it is preferable that the interval between the flat surface and the outer circumference of the rotating body 10 is set to a fourth interval (D) exceeding the second interval (B). At this time, it is more preferable that the flat surface is formed in a ring shape and is divided into a circular arc of a predetermined angle so as to form a complete ring shape when connected in the circumferential direction. It is preferable that such a flat surface is produced by centrifugal casting in the form of a ring and divided at a predetermined angle.

The second throttling portion is disposed between the first honeycomb chamber 130 and the brush chamber 140 and is formed by the first honeycomb 130a of the first honeycomb chamber 130, And the second gap distance G is set such that the fluid f decelerated at the second gap G is diffused and decelerated. The second gap G may be an axial gap between the first honeycomb chamber 130 and the brush chamber 140.

The third throttling portion is provided between the brush chamber 140 and the second honeycomb chamber 150 so that the fluid f reduced in pressure by the brush chamber 140 is diffused and decelerated, The distance G is preferable. The second gap distance G may be an axial distance between the brush chamber 140 and the second honeycomb chamber 150. The first honeycomb chamber 130 and the brush chamber 140 at the same spacing as the axial spacing.

Accordingly, a plurality of throttling portions are provided so as to be spread and decelerated to the entire area of the flow area during the flow of the fluid f at intervals between the guardian chambers 120, 160, the honeycomb chambers 130, 150 and the brush chamber 140 As the deceleration and the depressurization of the fluid are repeated, the kinetic energy of the fluid is drastically reduced, so that the sealing efficiency and performance of the device can be improved.

Further, the radial distance of each of the shunting portions is set to the fourth gap (D) exceeding the second gap (B) which is the radial gap between the honeycomb chambers (130, 150) As the distance E and the second gap G are set, the flow-in fluid f is diffused and stagnated to each of the throttle portions, so that kinetic energy is consumed and the sealing efficiency can be improved.

In the turbine composite sealing apparatus 100, the fluid f flows under reduced pressure when flowing into the first guardian part 120, and is diffused and decelerated at the first throttling part. Next, the fluid (f) is formed in the first honeycomb compartment (130) and is decelerated and flowed, and is diffused and decelerated at the second throttling part. The fluid (f) flows under reduced pressure by the brush chamber (140) and is diffused and decelerated at the third throttling portion. Then, the fluid (f) is reduced in flow velocity by the turbulent stagnation layer in the second honeycomb chamber (150), is diffused and decelerated at the fourth throttling portion, and is discharged under reduced pressure through the second guardian chamber (160). That is, the fluid (f) is repeatedly decelerated and decompressed in the process of flowing to the turbine composite sealing apparatus 100, and the kinetic energy is rapidly reduced.

Thus, each of the honeycomb chambers 130, 150 forming a turbulent stagnation layer to seal the flow of the fluid (f) flowing between the fixture 20 of the turbine and the rotator 10, The sealing performance of the apparatus and the rotation efficiency of the rotating body can be remarkably improved because the radial and axial fluid flow is substantially constrained by the combination and arrangement order of the brushes 120, 160 and the brush room 140.

7, the first guardian chamber 120 and the second guardian chamber 160 include a plurality of fluid slit holes 122 penetrating in the axial direction to increase the flow area of the fluid f, And a crown support 121 branched by the floating slit hole 122. [ At this time, the configuration of the floating slit hole 122 and the crown support 121 may be limited to the first guardian chamber 120 and may be the same as that of the first guardian chamber 120 and the second guardian chamber 160 . When the second guardian chamber 160 is applied only to the first guardian chamber 120, the second guardian chamber 160 is formed in a ring shape or a divided ring shape having a radially inner end opposite to the rotation axis 10, As shown in FIG. Hereinafter, the structure of the floating slit hole 122 and the crown supporting portion 121 will be described by taking the first guardian chamber 120 as an example.

In detail, the first guardian chamber 120 includes a ring-shaped base member 123 mounted on the sealing portion 110, and a plurality of crown supporting portions 123 radially projecting from a radially inner end of the base member 123 121). Accordingly, the first guardian chamber 120 can be easily attached to the sealing portion 110.

The gap between the radially inner end of the crown support 121 and the rotating body 10 is provided at the first gap A and the gap between the inner circumferential surface of the base member 123 and the rotating body 10 A sufficient interval exceeding the first spacing (A) is secured. That is, the floating slit hole 122 refers to a space between the crown supporting portions 121, and the crown supporting portions 121 are preferably spaced apart from each other at equal intervals in the circumferential direction. Accordingly, the radially inner end portions of the crown supporting portions 121 can be uniformly dispersed along the outer circumference of the rotating body 10.

As a result, the eccentric rotation of the rotating body 10 can be stably limited through the plurality of radially arranged crown supporting portions 121 while the substantial contact friction area is reduced. That is, while the frictional resistance is reduced, the reduction of the rotational force due to the vibration and the eccentric rotation can be prevented, and the rotation efficiency of the device can be improved.

The fluid flowing to the radially inner end of the crown support portion 121 and the rear of the first guardian chamber 120 is not limited to a narrow gap between the crown support portion 121 and the rotator 10, It can flow smoothly through the floating slit hole 122.

Specifically, when only a narrow gap corresponding to the second gap A is formed between the first guardian chamber 120 and the rotator 10, a restricted flow area causes a stagnation of the fluid flow, The vibration and eccentric rotation of the rotating body 10 may increase due to the compressive behavior due to the stagnation.

At this time, the eccentric rotation restricting function of the rotating body 10 is stably maintained through the crown supporting portion 121, and the fluid is stagnated or compressed through the floating slit hole 122 formed between the crown supporting portions 121, The behavior can be prevented. Preferably, the first guardian chamber 120 is installed to be deflected at a predetermined angle so that one crown support portion 121 is opposed to the other one of the floating slit holes 122.

5 and 7, the crown support portion 121 is provided such that the circumferential width decreases toward the inner side in the radial direction so as to reduce the friction area with respect to the outer circumference of the rotary body 10, It is preferable that the lubricant groove 121a is formed in the circumferential direction at the end portion. That is, the crown support 121 may be provided in a fan shape having a wide radial outer side in the circumferential direction and a narrow circumferential width toward the radially inner side.

The crown support portion 121 is rotatably supported on the outer circumference of the rotating body 10 while the crown supporting portion 121 is stably supported on the base member 123 with a wide supporting area, Can be reduced.

At this time, the lubricating groove 121a serves to reduce the friction area between the crown supporting portion 121 and the rotating body 10, and also to reduce the friction between the crown supporting portion 121 and the circumferential one- Thereby forming a fluid flow path connecting the slit holes.

That is, the high-pressure fluid flowing along the fluid slit hole 122 is instantaneously sucked into the inner space of the lubricant groove 121a, so that the gap between the radially inner end surface of the crown support portion 121 and the rotating body 10 A lubricant layer can be formed on the substrate. Accordingly, the contact friction between the crown support 121 and the rotating body 10 can be significantly reduced. In this case, it is more preferable that the lubricant hole 131a is formed in multiple stages in the axial direction according to the thickness of the crown support portion 121 in the axial direction.

Meanwhile, it is preferable that the fluid slit hole 122 is formed such that the circumferential width increases toward the radially inward side so that the fluid is concentrated on the outer circumferential side of the rotating body. That is, the floating slit hole 122 may be provided in a sector shape having a narrower circumferential width of the radially outer portion and a wider circumferential width toward the radially inner portion.

Accordingly, the fluid flowing from the front to the rear of the first guardian chamber 120 through the fluidic slit hole 122 can be concentrated and moved to the expanded space on the radially inward side of the fluidic slit hole 122 have. As a result, not only the crown supporting portion 121 but also the fluid passing through the floating slit hole 122 can provide a bearing force toward the radially inward side, so that the vibration and eccentricity of the rotating body 10 are remarkably reduced . The lubrication groove 121a formed at the radially inner end of the crown support 121 in the circumferential direction is communicated with the floating slit groove 132 and is concentrated to the lower portion of the floating slit hole 122 The fluid is compressed and introduced into the open circumferential both ends of the lubricating groove 121a to form a fluid lubricating layer, so that the frictional resistance between the crown supporter 121 and the rotating body 10 can be remarkably reduced.

The terms "comprises", "comprising", or "comprising" as used herein mean that a component can be implanted unless specifically stated to the contrary, But should be construed to include other elements. All terms, including technical and scientific terms, have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs, unless otherwise defined. Commonly used terms, such as predefined terms, should be interpreted to be consistent with the contextual meanings of the related art, and are not to be construed as ideal or overly formal, unless expressly defined to the contrary.

As described above, the present invention is not limited to the above-described embodiments, and variations and modifications may be made by those skilled in the art without departing from the scope of the present invention. And these modifications fall within the scope of the present invention.

100: Composite sealing device for turbine 110: Sealing part
120: first guardian room 130: first honeycomb room
140: Brush chamber 150: Second honeycomb chamber
160: 2nd Guardian Room

Claims (5)

A composite sealing device for a turbine mounted on an inner circumferential surface of a fixture facing a blade end of the rotator to seal a flow of fluid flowing between a fixture of the turbine and the rotator,
A first guardian disposed in the inflow direction of the fluid so that the fluid flows under reduced pressure through the throttling action, the first guardian being spaced apart at a predetermined first interval between the radially inner end and the outer periphery of the rotator, room;
And a second guardian seal disposed between the first guardian chamber and the outer circumference of the rotating body, And a plurality of first radially outwardly recessed first and second radially outwardly protruding radially outwardly facing radially inner surfaces of the first and second radially outwardly facing first and second radially outward surfaces of the rotating body so as to surround the rotating body at predetermined second intervals exceeding the first spacing, A first honeycomb chamber on which a honeycomb is formed;
Arranged so as to surround the rotating body at a predetermined third interval between the radially inner end and the outer periphery of the rotating body so that the reduced fluid flows under reduced pressure; and a second honeycomb filter A brush room including a bristle;
A plurality of second honeycomb grooves are formed to surround the rotating body at the second gap, the plurality of second honeycomb grooves being recessed radially outward along the inner circumferential surface opposed to the rotating body, A second honeycomb chamber; And
A second honeycomb filter disposed in the second honeycomb chamber in a direction in which the fluid flows in the first honeycomb chamber, the rotating body being wrapped around the first gap so as to restrict eccentric rotation of the rotating body due to a pressure deviation of the fluid, And a second guardian thread made of a low-hardness material having a hardness,
Wherein the first guardian chamber and the second guardian chamber include a plurality of flow slit holes axially penetrated to increase the flow area of the fluid and a crown support portion branched by the flow slit holes,
Wherein the crown support portion is formed such that the circumferential width decreases toward the radially inward direction so as to reduce the friction area with respect to the outer circumference of the rotating body, wherein a lubrication groove is formed in the radially inner end portion in the circumferential direction,
Wherein the floating slit hole is formed such that the circumferential width increases toward the radially inward side such that the fluid is concentrated to the outer circumferential side of the rotating body. The method according to claim 1,
Wherein the third gap is set to be less than the first gap so that the radially inner end of the brush seal is positioned adjacent to the rotator than the radially inner end of the first guardian chamber so that the fluid undergoes reduced pressure flow. Composite sealing device for turbines. The method according to claim 1,
A first gap distance between the first honeycomb chamber and the first honeycomb chamber and between the second honeycomb chamber and the second guardian chamber is set to a predetermined spacing distance in which an axial gap is set so as to spread and decelerate the fluid to the entirety of the flow area, ,
Between the first guardian chamber and the first honeycomb chamber and between the flat surface formed between the second honeycomb chamber and the second guardian chamber and the outer periphery of the rotator, Wherein a first throttle portion and a fourth throttle portion are formed at a fourth interval in which a radial distance exceeds the second gap. The method of claim 3,
And a second gap distance between the first honeycomb chamber and the brush chamber and between the brush chamber and the second honeycomb chamber such that the fluid is diffused and decelerated,
A second shaft portion having a radial gap between the first honeycomb chamber and the brush chamber and between the flat surface formed between the brush chamber and the second honeycomb chamber and the outer periphery of the rotating body, And a throttling portion are formed on the outer circumferential surface of the turbine. delete

Images