JP2006090273A - Fluid machine equipped with fluid sealing mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid machine having a very simple structure and capable of suppressing air leakage or gas leakage in a diffuser part and a turbine nozzle part of an exhaust turbo supercharger and preventing reduction of compressor performance or turbine performance due to air leakage or gas leakage. <P>SOLUTION: In the exhaust turbo supercharger provided with a diffuser 110 in an air outlet passage from a compressor wheel 101, a ringlike disc capable of being abutted on an end face of the diffuser 110 is provided, a clearance formed between the disc 11 and a case member is sealed by a ringlike sealing member 12, and the disc 11 and the diffuser 110 are abutted by pressure of air at a diffuser outlet which is introduced into the clearance to seal outlet air in the compressor wheel. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention is applied to an exhaust turbocharger, an industrial compressor, a gas turbine, and the like, and includes a diffuser that guides air compressed by the compressor wheel in an air outlet passage from the compressor wheel, or gas to the turbine wheel The present invention relates to a fluid machine having a fluid seal mechanism including a turbine nozzle in an inlet passage.

In an exhaust turbocharger having a diffuser that guides air compressed by the compressor wheel into an air outlet passage from the compressor wheel, air flows from a gap formed between the end surface of the diffuser and the compressor housing or the bearing housing. Leakage often occurs, and such air leakage often causes a problem that the supercharger performance is degraded.
FIG. 6B shows an example of a diffuser mounting portion in such an exhaust turbocharger. In the figure, 110 is a diffuser fixed to the bearing housing 106, and is an outlet of the compressor wheel 101 (see FIG. 6A). The air passage 111 communicates with the air passage 111 to guide the air flow in the air passage 111. A gap 020 having a minimum dimension S is formed between the end face of the diffuser 110 and the compressor housing 103 in consideration of a difference in thermal expansion.
The above-described air leakage occurs due to the air leakage through the gap 020.

A means shown in FIG. 6 (A) is provided as one means for preventing the deterioration of the supercharger performance due to such air leakage.
In such means, an annular disk 011 having an abutting surface that can be abutted against the end face of the diffuser 110 and being movably mounted on the diffuser 110 side is provided. A plurality of coil springs 023 are interposed between the back surface and the compressor housing 103, and the end face of the diffuser 110 and the contact surface of the disk 011 are always brought into contact with each other by the elasticity of the coil springs 023. The leak of the air compressed by 101 is suppressed. 101 a is a rotation axis of the compressor wheel 101.
Further, in a rotating body driven by an electric motor, means for minimizing a gap between the rotor and the casing in consideration of a difference in elongation due to thermal expansion of the rotor and the casing due to heat generated by the electric motor is disclosed in Japanese Patent Application Laid-Open No. 2001-234706. Issue).

JP 2001-234706 A

  However, in the means shown in FIG. 6A, a plurality of coil springs 023 are interposed between the back surface of the annular disk 011 incorporated in the compressor housing 103 and the compressor housing 103, and the coil springs 023 are arranged. The end face of the diffuser 110 and the contact surface of the disk 011 are pressed against each other by elasticity, and a gap 20 is formed between the back surface of the disk 011 on which the coil spring 023 is provided and the compressor housing 103. Thus, the air on the outlet side of the diffuser 110 leaks to the inlet side through the gap 20, and it is difficult to completely prevent the deterioration of the supercharger performance due to the air leakage in the diffuser 110 part.

Although not shown, the gap shown between the end surface of the turbine nozzle of the exhaust turbocharger and the turbine casing or the bearing housing is also applied to the gas shown in FIG. Although leakage is suppressed, in this case as well, it is difficult to completely prevent a decrease in supercharger performance due to gas leakage as described above.
And so on.

  In view of the problems of the prior art, the present invention suppresses air leakage or gas leakage in the diffuser part and the turbine nozzle part of the fluid machine with a very simple structure, and the compressor performance or It is an object of the present invention to provide a fluid machine including a fluid seal mechanism that prevents a decrease in turbine performance.

The present invention achieves such an object. In a fluid machine having a diffuser for guiding air compressed by a compressor wheel in an air outlet passage from the compressor wheel, the contact with the end face of the diffuser is made possible. An annular disk having a contact surface and a back surface facing the case member and incorporated in the case member so as to be movable toward the diffuser is provided, and a gap formed between the back surface of the disk and the case member is provided. An annular seal member made of an elastic body is provided that communicates with the air passage at the diffuser outlet and seals between the gap and the air passage at the compressor wheel outlet between the back surface of the disk and the case member. The pressure of the diffuser outlet air introduced into the gap causes the pressure between the contact surface of the disk and the diffuser. Is brought into contact with the surface, characterized by being configured to perform sealing of the compressor wheel outlet air.
In this invention, it is preferable that the seal member is composed of an O-ring made of rubber or resin.

  According to this invention, preferably a rubber or a gap is formed between the gap formed between the back surface of the annular disk incorporated in the case member movably on the diffuser side and the case member and the air passage at the compressor wheel outlet. Sealed with an elastic sealing member made of a resin O-ring, high pressure air at the diffuser outlet is introduced into the gap, and the pressure of the high pressure air brings the disk into contact with the end face of the diffuser. The high pressure air at the diffuser outlet can be supplied in a state of being completely sealed from the air passage at the compressor wheel outlet by the seal member.

Therefore, when the high-pressure air at the diffuser outlet is filled in the gap, the pressure of the high-pressure air allows the disk and the end face of the diffuser to always be in pressure contact, so that from the diffuser outlet side to the compressor wheel outlet side It is possible to reliably avoid air leakage to the compressor, and to prevent deterioration in compressor performance due to such air leakage.
Further, since the disk and the end face of the diffuser are brought into contact with each other by the pressure of the high-pressure air at the diffuser outlet in the gap, the gap and the compressor wheel outlet side are always sealed by a seal member without being affected by changes in engine operating conditions. The air leakage can be reliably avoided by the pressure difference between the pressure of the high-pressure air at the diffuser outlet and the pressure at the compressor wheel outlet in the gap.

Further, the present invention provides a fluid machine including a turbine nozzle in a gas inlet passage to a turbine wheel, and has a contact surface that can be contacted with an end surface of the turbine nozzle and a back surface that faces a case member. An annular disk incorporated in the case member so as to be movable toward the turbine nozzle side, and a gap formed between the back surface of the disk and the case member communicates with a gas passage at the turbine nozzle inlet; An annular seal member made of an elastic material that seals between the gap and the gas passage of the turbine wheel inlet is interposed between the back surface of the disk and the case member, and the turbine nozzle inlet of the turbine nozzle introduced into the gap is inserted. The turbine wheel inlet gas is sealed by bringing the abutting surface of the disk into contact with the end surface of the turbine nozzle by gas pressure. Characterized in that was.
In this invention, it is preferable that the seal member is composed of an elastically deformable metal O-ring.

  According to this invention, it is preferable that a gap formed between the back surface of the annular disk incorporated in the case member so as to be movable toward the turbine nozzle side and the case member, and the gas passage of the turbine wheel inlet. Sealing is performed with an elastic sealing member made of an elastically deformable metal O-ring, and a high-pressure gas at the turbine nozzle inlet is introduced into the gap so that the disk and the end face of the diffuser are brought into contact with each other by the pressure of the high-pressure gas. Therefore, the gas at the turbine wheel inlet can be supplied to the gap in a state of being completely sealed from the air passage at the turbine wheel inlet by the seal member.

Therefore, when the high pressure gas at the turbine nozzle inlet is filled in the gap, the disk and the end face of the diffuser can always be in pressure contact with each other by the pressure of the high pressure gas. Gas leakage to the inlet side can be reliably avoided, and deterioration in turbine performance due to such gas leakage can be prevented.
Further, since the disk and the end face of the diffuser are brought into contact with each other by the pressure of the high-pressure gas at the turbine nozzle inlet in the gap, the gap and the turbine are always sealed by a seal member without being affected by changes in operating conditions of the engine or the like. The gas leakage can be reliably avoided by the pressure difference between the pressure of the high-pressure gas at the turbine nozzle inlet and the pressure at the turbine wheel inlet in the gap while the space between the wheel inlet and the wheel is sealed.

In the two inventions, preferably, the seal member is arranged so that the mounting diameter of the seal member is smaller than the outer diameter of the diffuser or the outer diameter of the turbine nozzle.
If comprised in this way, the attachment part of the said sealing member will be arrange | positioned inside the outer periphery of a diffuser or the outer periphery of the said turbine nozzle, and the area of the clearance gap where high pressure air or high pressure gas is introduced will be taken to the maximum. And the pressure contact force between the disc and the end face of the diffuser can be maintained at the maximum value.

Preferably, in the two inventions, between the back surface of the disk and the case member, which is closer to the outer periphery than the seal member, the contact surface of the disk and the end surface of the diffuser or the contact surface of the disk and the A spring that presses against the end face of the turbine nozzle is interposed.
With this configuration, the contact surface of the disk and the end surface of the diffuser or the contact surface of the disk and the turbine are obtained by the combined force of the pressure of the high-pressure air or high-pressure gas introduced into the gap and the elasticity of the spring. The pressure contact force with the end face of the nozzle can be increased, and the effect of preventing air leakage from the diffuser outlet side to the compressor wheel outlet side and gas leakage from the turbine nozzle inlet side to the turbine wheel inlet side is further improved.

  According to the present invention, high-pressure air at the diffuser outlet is filled in the gap formed between the back surface of the annular disk incorporated in the case member so as to be movable toward the diffuser and the case member, and sealed with the seal member. In this state, the disk and the end face of the diffuser can always be brought into pressure contact with the pressure of the high-pressure air, so that air leakage from the diffuser outlet side to the compressor wheel outlet side can be reliably avoided.

  Further, according to the present invention, the high pressure gas at the inlet of the turbine nozzle is placed in a gap formed between the back surface of the annular disk incorporated in the case member so as to be movable toward the turbine nozzle and the case member and sealed by the seal member. In the filled state, the disk and the end face of the diffuser can always be brought into pressure contact with each other by the pressure of the high-pressure gas, thereby reliably preventing gas leakage from the turbine nozzle inlet side to the turbine wheel inlet side.

  As described above, according to the present invention, the gap formed between the back surface of the annular disk incorporated in the case member and the case member is sealed with the elastic seal member, and high pressure air or high pressure is sealed in the gap. Air leakage from the diffuser outlet side to the compressor wheel outlet side can be reliably avoided with a very simple structure of introducing gas and pressing the disk, and from the turbine nozzle inlet side to the turbine wheel inlet side. By making it possible to reliably avoid gas leakage to the air, it is possible to prevent deterioration of compressor performance or turbine performance due to such air leakage or gas leakage.

  Hereinafter, the present invention will be described in detail with reference to the embodiments shown in the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the component parts described in this example are not intended to limit the scope of the present invention only to specific examples unless otherwise specified. Only.

FIG. 5 is a cross-sectional view along the rotational axis of the exhaust turbocharger to which the fluid seal mechanism according to the first embodiment of the present invention is applied.
In FIG. 5, 104 is a turbine casing, 109 is a scroll passage formed in a spiral shape on the outer periphery of the turbine casing 104, and 113 is an exhaust gas outlet for sending exhaust gas expanded by the turbine rotor to the outside of the machine. It is. Reference numeral 112 denotes a gas inlet passage that leads from the scroll passage 109 to the gas inlet of the turbine wheel 102. Reference numeral 103 denotes a compressor housing, and 106 denotes a bearing housing that connects the compressor housing 103 and the turbine casing 104.
Reference numeral 102 denotes a turbine wheel, 101 denotes a compressor wheel, 105 denotes a turbine shaft that connects the turbine wheel 102 and the compressor wheel 101, and 107 and 108 denote bearings that are attached to the bearing housing 106 and support the turbine shaft 105. Reference numeral 101 a denotes a rotational axis of the turbine shaft 105.

Reference numeral 110 denotes an annular diffuser for guiding the air compressed by the compressor wheel 101, one end of which is fixed to the bearing housing 106 and installed in the air passage at the outlet of the compressor wheel 101. 111 b is a compressor outlet air passage that forms the inlet passage of the diffuser 110, and 111 a is a diffuser outlet air passage that forms the outlet passage of the diffuser 110.
Reference numeral 1 denotes a disk mechanism which forms the gist of the present invention.

During operation of such an exhaust turbocharger, exhaust gas introduced into the scroll passage 109 in the turbine casing 104 from an exhaust passage of an engine (not shown) passes through the gas inlet passage 112 from the outer periphery of the turbine wheel 102. After flowing into the wheel 102 and rotationally driving the turbine wheel 102, the turbine wheel 102 is discharged to the outside from the exhaust gas outlet 113.
The rotational force of the turbine wheel 102 is transmitted to the compressor wheel 101 via the turbine shaft 105, and the compressor wheel 101 compresses the air sucked through the air inlet passage 130. The compressed air is guided by the diffuser 110, is sent to an air supply port (not shown) of the engine through a passage inside the compressor housing 103, and is used for combustion.

FIG. 1 is a cross-sectional view of an essential part taken along a rotational axis of a fluid seal mechanism in a diffuser portion of an exhaust turbocharger according to a first embodiment of the present invention, and FIG.
1-2, 101 is a compressor wheel, 103 is a compressor housing, 106 is a bearing housing. Reference numeral 110 denotes an annular diffuser for guiding the air compressed by the compressor wheel 101, one end of which is fixed to the bearing housing 106 and installed in the air passage at the outlet of the compressor wheel 101. 111 b is a compressor outlet air passage that forms the inlet passage of the diffuser 110, and 111 a is a diffuser outlet air passage that forms the outlet passage of the diffuser 110.

Reference numeral 1 denotes a disk mechanism, which is configured as follows.
An annular disk 11 has a contact surface 11a that can be contacted with the end surface 110a of the diffuser 110, and a back surface 11b that faces the compressor housing 103, and moves to the diffuser 110 side. It is incorporated in the mounting groove 103 a of the compressor housing 103 as possible.
Reference numeral 20 denotes a gap formed between the back surface 11b of the disk 11 and the bottom surface of the mounting groove 103a of the compressor housing 103. The upper portion of the gap 20 communicates with the diffuser outlet air passage 111a. High-pressure air in the diffuser outlet air passage 111a is introduced.

Reference numeral 12 denotes an annular seal ring, which is composed of an O-ring made of rubber or resin, and in a ring groove 103b formed in the compressor housing 103, with a constant pressure between the back surface 11b of the disk 11 and the like. It is pushed in and seals between the gap 20 and the compressor outlet air passage 101b in a fluid-tight manner.
The mounting diameter D ₂ of the seal ring 12 is disposed the sealing ring 12 to be smaller than the inner periphery diameter Dt of the diffuser 110.
If comprised in this way, the area of the clearance gap 20 into which high pressure air is introduced can be maximized by arranging the mounting portion of the seal ring 12 closer to the inner periphery than the inner periphery of the diffuser 110. The pressure contact force between the disk 11 and the end face 110a of the diffuser 110 can be maintained at the maximum value.

Moreover, in FIG. 2, it is preferable to set the relationship between the attachment position of the said seal ring 12 and the main point of the said diffuser 110 as follows.
If D ₁ = the inner diameter of the disk 11, D ₂ = the mounting diameter of the seal ring 12, D ₃ = the outer diameter of the disk 11, D _l = the outer diameter of the diffuser 110, and D _t = the inner diameter of the diffuser 110,
D ₃ ≧ D _l
D _t ≧ D ₁
D ₂ ≦ (D ₁ + D ₃ ) / 2 or D ₂ ≦ D _l

According to the first embodiment, the gap 20 formed between the rear 11b and the compressor housing 103 of the annular disc 11 incorporated in movable compressor housing 103 to the diffuser 110 side, the pressure P ₂ becomes compressor The gap between the outlet air passages is preferably sealed by an elastic seal ring 12 made of an O-ring made of rubber or resin, and a pressure P ₁ higher than the pressure P ₂ is applied to the gap 20 from the diffuser outlet air passage 111a. High pressure air (21 is a high pressure air flow) is introduced, and the disk 11 and the end face of the diffuser 110 are brought into contact with each other by the pressure of the high pressure air. Therefore, the compressor ring air passage 111b is formed in the gap 20 by the seal ring 12. The high pressure air in the diffuser outlet air passage 111a in a completely sealed state It can supply.

Accordingly, when the gap 20 is filled with high-pressure air from the diffuser outlet air passage 111a, the contact surface 11a and the end surface 110a of the disk 11 and the diffuser 110 can always be pressed by the pressure of the high-pressure air. As a result, air leakage from the diffuser 110 outlet side to the compressor wheel 101 outlet side can be reliably avoided, and deterioration of the supercharger performance due to such air leakage can be prevented.
Further, since the disk 11 and the end face 110a of the diffuser 110 are brought into contact with each other by the pressure of high-pressure air from the diffuser outlet air passage 111a in the gap 20, the seal is always sealed without being affected by changes in engine operating conditions. The pressure difference between the pressure P ₁ of the high-pressure air at the outlet of the diffuser 110 and the pressure P ₂ at the outlet of the compressor wheel 101 in the gap 20 in a state where the gap 20 is sealed between the compressor outlet air passage 111 b side by the ring 12. The air leakage can be surely avoided by (P ₁ -P ₂ ).

FIG. 3 is a view corresponding to FIG. 1 showing a second embodiment of the present invention.
In this embodiment, in addition to the first embodiment, the contact of the disk 11 is between the back surface 11 b of the disk 11 and the mounting groove 103 a of the compressor housing 103, which is closer to the outer periphery than the seal ring 12. A coil spring 23 that presses the contact surface 11a and the end surface 110a of the diffuser 110 is interposed. A leaf spring may be used instead of the coil spring 23.
According to the second embodiment, the resultant force of the elastic force of the pressure P ₁ and the coil spring 23 of high-pressure air introduced into the gap 20, between the end surface 110a of the diffuser 110 and the abutment surface 11a of the disk 11 Therefore, the effect of preventing air leakage from the diffuser outlet air passage 111a side to the compressor outlet air passage 111b side is further improved.
Other configurations and operational effects are the same as those of the first embodiment, and the same members are denoted by the same reference numerals.

FIG. 4 is a cross-sectional view of the main part along the rotational axis of the fluid seal mechanism in the turbine nozzle portion of the exhaust turbocharger according to the third embodiment of the present invention.
In FIG. 4, 102 is a turbine wheel, 25 is a turbine nozzle, 104 is a turbine casing, and 106 is a bearing housing. 112a is a turbine nozzle inlet gas passage, and 112b is a turbine wheel inlet gas passage.

Reference numeral 1 denotes a disk mechanism, which is configured as follows.
11 is a disk formed in an annular shape, and has a contact surface 11a that can be contacted with an end surface 25a of the turbine nozzle 25 and a back surface 11b that faces the turbine casing 104. It is incorporated in the mounting groove 104a of the turbine casing 104 so as to be movable.
Reference numeral 20 denotes a gap formed between the back surface 11b of the disk 11 and the bottom surface of the mounting groove 104a of the turbine casing 104. The upper portion of the gap 20 communicates with the turbine nozzle inlet gas passage 112a. The high-pressure gas in the turbine nozzle inlet gas passage 112a is introduced into the turbine nozzle inlet gas passage 112a.

Reference numeral 12 denotes a ring-shaped seal ring, which is composed of a heat-resistant metal O-ring (this O-ring itself is known), and in the ring groove 104b formed in the turbine casing 104, The disk 11 is pushed into the back surface 11b of the disk 11 with a constant pressure, and the gap 20 and the turbine wheel inlet gas passage 112b are sealed in a fluid-tight manner.
The seal ring 12 is arranged so that the mounting diameter of the seal ring 12 is smaller than the inner peripheral diameter of the turbine nozzle 25.
If comprised in this way, the area of the clearance gap 20 into which high-pressure air is introduced can be maximized by arranging the mounting portion of the seal ring 12 closer to the inner periphery than the inner periphery of the turbine nozzle 25. Thus, the pressure contact force between the disk 11 and the end face 25a of the turbine nozzle 25 can be maintained at the maximum value.

According to the third embodiment, the gap 20 formed between the rear 11b and the turbine casing 104 of the annular disc 11 incorporated in movable turbine casing 104 to a turbine nozzle 25, the pressure P ₄ becomes turbine between the wheel inlet gas passage 112b and sealed with the seal ring 12 of the elastic body, the high pressure high pressure gas (26 high pressure gas stream comprising the pressure P ₃ than the pressure P ₄ from the turbine nozzle inlet gas passage 112a to the clearance 20 ) And the disk 11 and the end face of the turbine nozzle 25 are brought into contact with each other by the pressure of the high-pressure gas, so that the gap 20 is completely sealed from the turbine wheel inlet gas passage 112b by the seal ring 12. The high-pressure gas in the turbine nozzle inlet gas passage 112a can be supplied.

Therefore, with the gap 20 filled with the high pressure gas from the turbine nozzle inlet gas passage 112a, the disk 11 and the end surface 25a of the turbine nozzle 25 can always be in pressure contact with each other by the pressure of the high pressure gas. As a result, air leakage from the turbine nozzle 25 inlet side to the turbine wheel 102 inlet side can be reliably avoided, and deterioration of the supercharger performance associated with such air leakage can be prevented.
Further, since the disk 11 and the end face 25a of the turbine nozzle 25 are brought into contact with each other by the pressure of the high-pressure gas from the turbine nozzle inlet gas passage 112a in the gap 20, without being affected by changes in engine operating conditions, by constantly seal ring 12 in a state between the sealed between the gap 20 and the turbine wheel inlet gas passage 112b, the pressure P ₃ and the turbine wheel 102 the inlet of the pressure P ₄ of the high pressure gas turbine nozzle 25 inlet within the gap 20 The gas leakage can be surely avoided by the pressure difference (P ₃ -P ₄ ).

  Although not shown, in addition to the third embodiment of FIG. 4, as in the second embodiment of FIG. 3, the rear surface 11 b of the disk 11 and the turbine casing closer to the outer periphery than the seal ring 12. A coil spring 23 (or a leaf spring) that presses the contact surface 11 a of the disk 11 and the end surface 25 a of the turbine nozzle 25 may be interposed between the mounting groove 104 a of 104.

  In each of the above embodiments, the present invention is applied to an exhaust turbocharger. However, the present invention is not limited to these, and is also applied to industrial compressors, gas turbine compressors and turbines, various expanders, and the like. it can.

  According to the present invention, air leakage or gas leakage in the diffuser portion and turbine nozzle portion of the exhaust turbocharger can be suppressed with an extremely simple structure, and compressor performance or turbine performance due to such air leakage or gas leakage can be suppressed. It is possible to provide a fluid machine that prevents the decrease.

It is principal part sectional drawing in alignment with the rotating shaft center line of the fluid seal mechanism in the diffuser part of the exhaust turbo supercharger which concerns on 1st Example of this invention. It is the Z section enlarged view of FIG. 1 in the said 1st Example. FIG. 3 is a view corresponding to FIG. 1 showing a second embodiment of the present invention. It is principal part sectional drawing in alignment with the rotating shaft center line of the fluid seal mechanism in the turbine nozzle part of the exhaust turbo supercharger which concerns on 3rd Example of this invention. It is sectional drawing which follows the rotating shaft center line of the exhaust gas turbocharger to which 1st Example of this invention is applied. FIG. 1A is a diagram corresponding to FIG. 1 showing a first example of the prior art, and FIG.

Explanation of symbols

101 Compressor wheel 102 Turbine wheel 103 Compressor housing 104 Turbine casing 106 Bearing housing 110 Diffuser 111a Diffuser outlet air passage 111b Compressor outlet air passage,
112a Turbine nozzle inlet gas passage 112b Turbine wheel inlet gas passage 1 Disc mechanism 11 Disc 12 Seal ring 20 Clearance 23 Coil spring

Claims (6)

  In a fluid machine having a diffuser for guiding air compressed by a compressor wheel in an air outlet passage from the compressor wheel, the fluid machine has a contact surface capable of contacting the end surface of the diffuser and a back surface facing the case member. An annular disk incorporated in the case member so as to be movable toward the diffuser, and a gap formed between the back surface of the disk and the case member communicates with the air passage at the diffuser outlet, An annular seal member made of an elastic material that seals between the gap and the air passage of the compressor wheel outlet is interposed between the back surface of the disk and the case member, and the diffuser outlet introduced into the gap Compressor wheel is brought into contact with the abutting surface of the disk and the end surface of the diffuser by air pressure. Fluid machine comprising a fluid sealing mechanism, characterized by being configured to perform sealing of the outlet air.   2. A fluid machine having a fluid seal mechanism according to claim 1, wherein the seal member is made of an O-ring made of rubber or resin.   In a fluid machine equipped with a turbine nozzle in a gas inlet passage to a turbine wheel, it has a contact surface that can be contacted with an end surface of the turbine nozzle and a back surface that faces a case member, and can move to the turbine nozzle side. And an annular disk incorporated in the case member, and a gap formed between the back surface of the disk and the case member communicates with a gas passage at the turbine nozzle inlet, and the back surface of the disk and the case An annular sealing member made of an elastic body that seals between the gap and the gas passage at the turbine wheel inlet is interposed between the members, and the disk is caused by the pressure of the gas at the inlet of the turbine nozzle introduced into the gap. The abutment surface of the turbine and the end surface of the turbine nozzle are brought into contact with each other to seal the turbine wheel inlet gas. Fluid machine comprising a fluid sealing mechanism that.   2. The fluid machine having a fluid seal mechanism according to claim 1, wherein the seal member is made of an elastically deformable metal O-ring.   4. The seal member according to claim 1, wherein the seal member is arranged so that an attachment diameter of the seal member is smaller than an outer peripheral diameter of the diffuser or an outer peripheral diameter of the turbine nozzle. 5. A fluid machine equipped with a fluid seal mechanism.   A spring that presses the contact surface of the disk and the end surface of the diffuser or the contact surface of the disk and the end surface of the turbine nozzle between the back surface of the disk and the case member closer to the outer periphery than the seal member. A fluid machine equipped with a fluid seal mechanism according to any one of claims 1 and 3.

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