JP6384751B2 - Turbo compressor and rotary ring position restriction nut - Google Patents

Description

  The present invention relates to a turbo compressor and a rotary ring position regulating nut.

  Turbo compressors are used to compress various fluids and may handle, for example, corrosive gases. In general, the impeller can be made of a material having high corrosion resistance against corrosive gas, but the shaft that transmits rotational power to the impeller is made of such a high corrosion resistance material in relation to other mechanisms. It may be difficult to form. For this reason, for example, as shown in Patent Document 1, the shaft is prevented from corroding by covering the shaft with a double sleeve.

JP 2000-9091 A

  However, according to the method of Patent Document 1, it is necessary to divide the sleeve into an inner sleeve and an outer sleeve, which leads to an increase in the number of parts. Therefore, in the method of Patent Document 1, the assembly work is complicated and the reliability is lowered due to an increase in the number of parts.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to reliably prevent corrosion of a shaft while suppressing an increase in the number of parts in a turbo compressor.

  The present invention adopts the following configuration as means for solving the above-described problems.

  According to a first aspect of the present invention, an impeller that compresses a fluid to be compressed, a housing that houses the impeller, a shaft that is connected to the impeller inside the housing, and the shaft is disposed so as to surround the shaft. A turbo compressor including a dry gas seal mechanism for preventing leakage of the fluid to be compressed along the shaft, the turbo compressor being provided inside the casing and provided on the impeller side of the rotary ring provided in the dry gas seal mechanism A rotating ring restricting member for restricting the movement of the shaft, and the rotating ring restricting member covers the entire peripheral surface of the tip end portion of the shaft located inside the housing and is more resistant to the compressed fluid than the shaft. A configuration in which it is formed of a high material is adopted.

  According to a second invention, in the first invention, the rotary ring restricting member is an annular member that is screwed into a tip portion of the shaft.

  According to a third invention, in the second invention, the impeller has a connecting portion connected to the shaft, and the rotating ring regulating member has an extending portion extending to the connecting portion of the impeller. A configuration is adopted in which a gasket interposed between the extending portion and the connecting portion is provided.

  In a fourth aspect based on the third aspect, the rotating ring restricting member is provided on the rotating ring side with respect to the extending portion and has a large diameter portion that is larger in diameter than the extending portion. And the structure that the said extension part is thinned to radial direction rather than the said large diameter part is employ | adopted.

  According to a fifth aspect of the invention, there is provided an impeller that compresses a fluid to be compressed and a dry gas seal that is screwed into a tip portion of a shaft that is connected inside a casing that houses the impeller and that is disposed around the shaft. A rotary ring position restricting nut for restricting movement of the rotary ring included in the mechanism toward the impeller side, covering the entire peripheral surface of the tip portion of the shaft located inside the housing, and more A configuration in which the material is formed of a material having high corrosion resistance to the compressed fluid is employed.

  According to the present invention, the rotating ring restricting member (rotating ring position restricting nut) for restricting the movement of the rotating ring of the dry gas seal mechanism is formed of a material having higher corrosion resistance against the fluid to be compressed than the shaft. The entire circumferential surface of the tip portion of the shaft is covered with the rotating ring restricting member. That is, in the present invention, a function of protecting the shaft from the fluid to be compressed is added to the rotating ring regulating member. For this reason, according to this invention, it becomes possible to prevent corrosion of a shaft reliably, without increasing a number of parts.

1 is an overall view schematically showing a schematic configuration of a turbo compressor in an embodiment of the present invention. It is sectional drawing to which the vicinity of the connection location of the shaft and impeller of the turbo compressor in one Embodiment of this invention was expanded. It is a perspective view of the rotary ring position control nut with which the turbo compressor in one embodiment of the present invention is provided. (A) is the further enlarged view of FIG. 2 containing the rotation prevention washer with which the turbo compressor in one Embodiment of this invention is provided, (b) is a perspective view of a rotation prevention washer.

  Hereinafter, an embodiment of a turbo compressor and a rotary ring position regulating nut according to the present invention will be described with reference to the drawings. In the following drawings, the scale of each member is appropriately changed in order to make each member a recognizable size.

  First, with reference to FIG. 1, the outline | summary of the turbo compressor 1 of this embodiment is demonstrated. FIG. 1 is an overall view schematically showing a schematic configuration of a turbo compressor 1 of the present embodiment. As shown in this figure, the turbo compressor 1 of the present embodiment includes a motor 2, a transmission unit 3, a shaft 4, an impeller 5, a housing 6, a seal plate 7, a dry gas seal mechanism 8, A recovery device 9 and a nitrogen supply device 10 are provided.

  The motor 2 generates power for rotationally driving the impeller 5. The transmission unit 3 transmits the rotational power generated by the motor 2 to the shaft 4 and includes a gear (not shown), a housing for housing the gear, and the like. The shaft 4 has a tip connected to the impeller 5 and transmits the rotational power generated by the motor 2 to the impeller 5. The impeller 5 is a radial impeller housed inside the housing 6, and compresses the corrosive gas X (compressed fluid) sucked into the housing 6. The impeller 5 is formed of a material (for example, titanium alloy) having high corrosion resistance against the corrosive gas X, and discharges the corrosive gas X supplied from the axial direction toward the radially outer side. The housing 6 covers the impeller 5 from the side, and has a flow path of the corrosive gas X inside. The housing 6 is open on the back side of the impeller 5. The seal plate 7 is fixed to the housing 6 so as to close the open portion of the housing 6, and is arranged with a certain gap with respect to the back surface of the impeller 5. The housing 6 and the seal plate 7 constitute a housing of the present invention that houses the impeller 5. The dry gas sealing mechanism 8 is disposed so as to surround the shaft 4 and prevents leakage of the corrosive gas X from the inside of the housing 6 along the shaft 4 to the transmission unit 3 side. The recovery device 9 recovers the return gas from the dry gas seal mechanism 8. The nitrogen supply device 10 supplies nitrogen gas to the dry gas sealing mechanism 8.

  In the turbo compressor 1 of this embodiment, the impeller 5 is rotationally driven by transmitting the rotational power generated by the motor 2 to the impeller 5 through the transmission unit 3 and the shaft 4. As a result, the corrosive gas X supplied into the housing 6 is compressed and then discharged from the housing 6. At this time, the dry gas sealing mechanism 8 prevents the corrosive gas X from leaking from the inside of the housing 6 to the transmission unit 3 side.

  Then, with reference to FIGS. 2-4, the characteristic part of the turbo compressor 1 of this embodiment is demonstrated.

  FIG. 2 is an enlarged cross-sectional view of the vicinity of the connection portion between the shaft 4 and the impeller 5 of the turbo compressor 1 of the present embodiment. As shown in this figure, the shaft 4 is provided so as to penetrate the seal plate 7, and a gap between the seal plate 7 and the back surface of the impeller 5 (that is, a housing constituted by the housing 6 and the seal plate 7). The tip portion 4a is located inside. The distal end portion 4a is formed with a male screw 4b on the peripheral surface thereof, into which a rotating ring position regulating nut 11 described later is screwed. The impeller 5 includes a connecting portion 5a that bulges in the axial direction at the center of the back surface. The connecting portion 5 a is a portion that is connected to the shaft 4. An annular groove 5b for positioning an O-ring 12 (gasket), which will be described later, is provided on the peripheral surface of the connecting portion 5a. The front end surface of the shaft 4 on the impeller 5 side and the front end surface of the connecting portion 5a of the impeller 5 are provided with a plurality of teeth that mesh with each other, and the shaft 4 and the impeller 5 are connected by a carbide coupling mechanism. ing.

  The dry gas seal mechanism 8 includes a seal case 8a, a first sleeve 8b, a first rotating ring 8c, a first fixed ring 8d, a first holder 8e, a second sleeve 8f, and a second rotating ring 8g. The second fixed ring 8h, the second holder 8i, the third rotating ring 8j, the third fixed ring 8k, and the third holder 8l are provided.

  The seal case 8a includes a first sleeve 8b, a first rotary ring 8c (rotary ring), a first fixed ring 8d, a first holder 8e, a second sleeve 8f, a second rotary ring 8g, a second fixed ring 8h, and a second This is a cylindrical case surrounding the holder 8i, the third rotating ring 8j, the third fixed ring 8k, and the third holder 8l. The seal case 8a is fixed to the seal plate 7, and is disposed so as to surround the shaft 4 on the transmission portion 3 side with respect to the tip portion 4a.

  The first sleeve 8b is an annular member disposed closest to the impeller 5 inside the seal case 8a, and is disposed with a certain gap with respect to the inner peripheral surface of the seal case 8a. The first sleeve 8 b is fixed to the shaft 4 with its inner peripheral surface being in contact with the shaft 4 and the peripheral surface, and rotates with the shaft 4. The first rotary ring 8c is an annular member fixed to the first sleeve 8b, and the surface on the transmission portion 3 side can be brought into contact with the surface on the impeller 5 side of the first fixed ring 8d. Since the first rotating ring 8 c is fixed to the first sleeve 8 b, it rotates with the shaft 4.

  The first fixed ring 8d is an annular member fixed to the seal case 8a via the first holder 8e, and the surface on the impeller 5 side is the surface on the transmission portion 3 side of the first rotating ring 8c as described above. It is possible to abut. The first holder 8e is fixed to the seal case 8a, and supports the first fixed ring 8d while urging it toward the impeller 5 side. Such a first stationary ring 8d is moved so as to be slightly separated from the first rotating ring 8c by the dynamic pressure generated when the first rotating ring 8c rotates with the shaft 4. As a result, a gap flow path through which the corrosive gas X flows is formed between the first rotating ring 8c and the first fixed ring 8d.

  The second sleeve 8f is an annular member that is disposed closer to the transmission portion 3 than the first sleeve 8b inside the seal case 8a, and is disposed with a certain gap with respect to the inner peripheral surface of the seal case 8a. . The second sleeve 8 f is fixed to the shaft 4 with the inner peripheral surface being in contact with the shaft 4, and rotates with the shaft 4. The second rotating ring 8g is an annular member fixed to a portion on the impeller 5 side of the second sleeve 8f, and the surface on the impeller 5 side can be brought into contact with the surface on the transmitting portion 3 side of the second fixed ring 8h. ing. The third rotating ring 8j is an annular member fixed to a portion of the second sleeve 8f on the transmitting portion 3 side, and the surface on the transmitting portion 3 side can come into contact with the surface on the impeller 5 side of the third fixing ring 8k. Has been. Since the second rotary ring 8g and the third rotary ring 8j are fixed to the second sleeve 8f, they rotate with the shaft 4.

  The second fixed ring 8h is an annular member fixed to the seal case 8a via the second holder 8i, and the surface on the transmission unit 3 side is the surface on the impeller 5 side of the second rotary ring 8g as described above. It is possible to abut. The second holder 8i is fixed to the seal case 8a, and supports the second fixed ring 8h while urging it toward the transmitting portion 3. Such a second stationary ring 8h is moved so as to be slightly separated from the second rotating ring 8g by the dynamic pressure generated when the second rotating ring 8g rotates along with the shaft 4. As a result, a gap channel through which the nitrogen gas Y flows is formed between the second rotating ring 8g and the second fixed ring 8h.

  The third fixed ring 8k is an annular member fixed to the seal case 8a via the third holder 8l. As described above, the surface on the impeller 5 side is the surface on the transmission portion 3 side of the third rotating ring 8j. It is possible to abut. The third holder 8l is fixed to the seal case 8a, and supports the third fixed ring 8k while urging it toward the impeller 5 side. The third fixed ring 8k is moved so as to be slightly separated from the third rotary ring 8j by the dynamic pressure generated when the third rotary ring 8j rotates with the shaft 4. As a result, a gap channel through which the nitrogen gas Y flows is formed between the third rotating ring 8j and the third fixed ring 8k.

  According to such a dry gas seal mechanism 8, when the shaft 4 rotates, a gap flow path through which the corrosive gas X flows is formed between the first rotating ring 8 c and the first fixed ring 8 d, and the second rotating ring. A gap channel through which nitrogen gas Y flows is formed between 8g and the second stationary ring 8h, and a gap channel through which nitrogen gas Y flows is formed between the third rotating ring 8j and the third stationary ring 8k. . At this time, the corrosive gas X is directly or mixed with the nitrogen gas Y and recovered by the recovery device 9. Further, a part of the nitrogen gas Y is mixed with the corrosive gas X and recovered by the recovery device 9, and the rest leaks to the transmission unit 3 side. For this reason, the dry gas sealing mechanism 8 prevents the corrosive gas X from being exposed to the transmission unit 3 side.

  As shown in FIG. 2, the turbo compressor 1 according to the present embodiment includes a rotating ring position restricting nut 11 (rotating ring restricting member). FIG. 3 is a perspective view of the rotary ring position regulating nut 11. As shown in this figure, the rotary ring position regulating nut 11 has a shape in which a large diameter portion 11a and an extending portion 11b are integrated. The large diameter portion 11a is an annular portion having an opening 11c having a diameter slightly larger than the diameter of the shaft 4, and has a larger diameter than the extending portion 11b. Two grooves 11d are provided on the outer peripheral surface of the large-diameter portion 11a at opposing positions with the opening 11c interposed therebetween. These grooves 11d are provided so as to penetrate the large-diameter portion 11a in the same direction as the penetration direction of the opening 11c. Further, the width of these grooves 11d (the size in the circumferential direction of the large diameter portion 11a) is set slightly wider than the width of the tongue portion 13b of the anti-rotation washer 13 described later. Such a large diameter portion 11a is provided on the dry gas seal mechanism 8 side (that is, the first rotating ring 8c) from the extending portion 11b when the rotating ring position regulating nut 11 is attached to the shaft 4 as shown in FIG. Side).

  The extending portion 11b has a cylindrical shape having an opening 11e having the same diameter as the large-diameter portion 11a, and the large-diameter portion so that the opening 11e communicates linearly with the opening 11c of the large-diameter portion 11a. 11a. The extending portion 11b is thinner in the radial direction than the large diameter portion 11a. Further, the length of the extending portion 11b is such that the groove 5b (see FIG. 5) provided on the peripheral surface of the connecting portion 5a of the impeller 5 when the rotary ring position regulating nut 11 is attached to the shaft 4 as shown in FIG. 2).

  Female threads 11f are provided on the inner peripheral surface of these large diameter portions 11a and the inner peripheral surface of the extending portion 11b from the large diameter portion 11a side toward the extending portion 11b. The female screw 11 f is screwed with a male screw 4 b provided at the tip portion 4 a of the shaft 4.

  The rotating ring position regulating nut 11 formed by integrating the large diameter portion 11 a and the extending portion 11 b is formed of a material having higher corrosion resistance against the corrosive gas X than the shaft 4. For example, when the corrosive gas X is methyl acetate and the shaft 4 is formed of nickel chrome molybdenum steel, the forming material of the rotating ring position regulating nut 11 is stainless steel having higher corrosion resistance than nickel chrome molybdenum steel. Formed by.

  Such a rotary ring position regulating nut 11 has a shaft with the large-diameter portion 11a facing the dry gas seal mechanism 8 when the female screw 11f is screwed into the male screw 4b provided at the tip portion 4a of the shaft 4. 4 is fixed. The rotating ring position regulating nut 11 fixed in this way is arranged so that the large diameter portion 11a comes into contact with the first sleeve 8b of the dry gas seal mechanism 8 from the impeller 5 side via a rotation prevention washer 13 described later. The movement of the first rotary ring 8c toward the impeller 5 is restricted. Further, as shown in FIG. 2, the rotating ring position regulating nut 11 covers the entire peripheral surface of the tip end portion 4 a of the shaft 4 in a state where it is attached to the shaft 4, whereby the corrosive gas X touches the shaft 4. To prevent that.

  Thus, the rotary ring position regulating nut 11 is an annular member that is screwed into the tip end portion 4a of the shaft 4, and is provided inside the housing constituted by the housing 6 and the seal plate 7, and is provided with a dry gas seal. The movement of the first rotating ring 8c included in the mechanism 8 toward the impeller 5 is restricted. Further, the rotary ring position regulating nut 11 is formed of a material that covers the entire peripheral surface of the tip portion 4 a of the shaft 4 and has higher corrosion resistance against the corrosive gas X than the shaft 4.

  Moreover, the turbo compressor 1 of this embodiment is provided with the O-ring 12 (gasket) as shown in FIG. The O-ring 12 is disposed in a groove 5 b provided in the connecting portion 5 a of the impeller 5, and is interposed between the connecting portion 5 a of the impeller 5 and the extending portion 11 b of the rotary ring position regulating nut 11. Yes. The O-ring 12 prevents the corrosive gas X from entering between the connecting portion 5 a of the impeller 5 and the extending portion 11 b of the rotating ring position regulating nut 11.

  Moreover, the turbo compressor 1 of this embodiment is provided with the rotation prevention washer 13 as shown in FIG. FIG. 4A is a further enlarged view of FIG. 2 including the anti-rotation washer 13. FIG. 4B is a perspective view of the rotation prevention washer 13.

  As shown in these drawings, the rotation prevention washer 13 is a washer interposed between the first sleeve 8b of the dry gas seal mechanism 8 and the rotation ring position regulating nut 11, and is shown in FIG. 4B. Thus, the projection part 13a provided in the radial direction center side, and the tongue part 13b provided in the outer edge part are provided. Two each of these protrusions 13a and tongues 13b are provided across a central opening 13c through which the shaft 4 passes.

  As shown in FIG. 4A, the first sleeve 8 b of the dry gas seal mechanism 8 can be engaged with the protrusion 13 a of the rotation prevention washer 13 and can move the protrusion 13 a in the circumferential direction of the shaft 4. A locking groove 8b1 for restriction is provided. The anti-rotation washer 13 is disposed so as to abut against the surface of the first sleeve 8b on the impeller 5 side so that the protrusion 13a is locked in the locking groove 8b1. In this way, the protrusion 13 a is locked in the locking groove 8 b 1, whereby the position of the rotation preventing washer 13 is restricted so as not to be displaced in the circumferential direction with respect to the shaft 4.

  As shown by a two-dot chain line in FIG. 4B, the tongue portion 13 b is not bent before assembling, and protrudes toward the radially outer side of the anti-rotation washer 13. These tongue portions 13b are arranged so that the rotation prevention washer 13 is locked in the locking groove 8b1 of the first sleeve 8b, and then the rotation ring position regulating nut 11 is screwed into the tip portion 4a of the shaft 4, The restriction nut 11 is bent so as to be fitted into a groove 11d provided in the large diameter portion 11a. In this manner, the tongue 13b of the rotation prevention washer 13 is bent and fitted into the groove 11d provided in the large diameter portion 11a of the rotation ring position regulating nut 11, so that the rotation prevention washer 13 is rotated at the rotation ring position. The position is regulated so as not to be displaced in the circumferential direction relative to the regulating nut 11.

  In this way, the position of the rotation prevention washer 13 is restricted with respect to the shaft 4 and the rotation ring position restriction nut 11, so that the shaft 4 and the rotation ring position restriction nut 11 are circumferentially arranged via the rotation prevention washer 13. Fixed.

  According to the turbo compressor 1 of this embodiment, the rotary ring position restriction nut 11 that restricts the movement of the first rotary ring 8 c of the dry gas seal mechanism 8 is more resistant to the corrosive gas X than the shaft 4. The rotary ring position restricting nut 11 covers the entire peripheral surface of the tip portion 4a of the shaft 4. That is, in this embodiment, the function of protecting the shaft 4 from the corrosive gas X is added to the rotary ring position regulating nut 11. For this reason, according to the turbo compressor 1 of the present embodiment, it is possible to reliably prevent the corrosion of the shaft without increasing the number of parts.

  Further, in the turbo compressor 1 of the present embodiment, the rotary ring position regulating nut 11 is an annular member that is screwed into the tip portion 4 a of the shaft 4. For this reason, the rotary ring position regulating nut 11 can be easily fixed to the shaft 4. Further, the inner circumferential surface of the rotary ring position regulating nut 11 and the circumferential surface of the shaft 4 are brought into contact with each other, and the corrosive gas X can be prevented from entering between the rotary ring position regulating nut 11 and the shaft 4. it can.

  Further, in the turbo compressor 1 of the present embodiment, the extending portion 11b of the rotary ring position regulating nut 11 extends to the connecting portion 5a of the impeller 5, and an O-ring is provided between the extending portion 11b and the connecting portion 5a. 12 is interposed. For this reason, it is possible to more reliably prevent the corrosive gas X from entering between the rotary ring position regulating nut 11 and the shaft 4.

  Further, in the turbo compressor 1 of the present embodiment, the rotary ring position regulating nut 11 is provided on the first rotary ring 8c side with respect to the extending portion 11b and has a larger diameter than the extending portion 11b. 11a. Further, the extending part 11b is thinner in the radial direction than the large diameter part 11a. When the rotating ring position restricting nut 11 is rotated along with the shaft 4, the rotating ring position restricting nut 11 is expanded outward in the radial direction by centrifugal force. At this time, the centrifugal force acts greatly on a portion having a large mass. For this reason, the centrifugal force which acts on the extension part 11b can be weakened by thinning the extension part 11b to radial direction. As a result, the amount by which the extending portion 11b swells can be reduced, and the corrosive gas X can be more reliably prevented from entering between the extending portion 11b and the connecting portion 5a.

As mentioned above, although preferred embodiment of this invention was described referring an accompanying drawing, it cannot be overemphasized that this invention is not limited to the said embodiment. Various shapes, combinations, and the like of the constituent members shown in the above-described embodiments are examples, and various modifications can be made based on design requirements and the like without departing from the spirit of the present invention.
For example, in the above embodiment, the dry gas seal mechanism 8 includes a plurality of rotating rings (first rotating ring 8c, second rotating ring 8g, and third rotating ring 8j), and a plurality of fixed rings (first fixed ring 8d, The configuration including the second stationary ring 8h and the third stationary ring 8k) has been described. However, the present invention is not limited to this, and can be applied to other configurations as long as the turbo compressor includes a dry gas seal mechanism including a stationary ring.

  Moreover, in the said embodiment, the structure which is the rotation ring position control nut 11 screwed in the shaft 4 demonstrated the rotation ring control member of this invention. However, the present invention is not limited to this. For example, it is possible to use a rotary ring restricting member fixed to a constituent member other than the shaft 4 such as the seal plate 7.

  Moreover, in the said embodiment, the structure by which the extension part 11b was thinned was demonstrated. However, the present invention is not limited to this, and the amount of deformation during rotation of the rotary ring position regulating nut 11 is small, and the corrosive gas X may enter between the extending portion 11b and the connecting portion 5a. If not, the extending portion 11b need not be thinned. Further, when the amount of deformation during rotation of the rotary ring position regulating nut 11 is small as described above, the O-ring 12 can be omitted.

  Moreover, the present invention that has been described with the above embodiment as a specific example can also be expressed as follows, and this is naturally included in the scope of the present invention. That is, the turbo compressor according to the present invention includes a casing, a shaft provided in the casing, an impeller connected to the shaft, and provided in the casing and connected to the shaft. The shaft covers the shaft between a dry gas seal mechanism including a rotating ring and the impeller and the dry gas seal mechanism, and is fixed to the shaft in contact with the dry gas seal mechanism, and is more corrosive than the shaft. And a rotating ring restricting member formed of a material having high corrosion resistance to gas.

  The rotating ring restricting member is an annular member screwed to the shaft between the impeller and the dry gas seal mechanism.

  The rotation restricting member includes a first portion including a portion that contacts the dry gas sealing mechanism, and a second portion that is between the first portion and the impeller and has a smaller diameter than the first portion. .

  Furthermore, it has an anti-rotation washer provided between the rotary ring restricting member and the dry gas seal mechanism.

  As described above, the present invention can be described in this way.

  DESCRIPTION OF SYMBOLS 1 ... Turbo compressor, 2 ... Motor, 3 ... Transmission part, 4 ... Shaft, 4a ... Tip part, 4b ... Male screw, 5 ... Impeller, 5a ... Connection part, 5b ... Groove , 6 ... Housing, 7 ... Seal plate, 8 ... Dry gas seal mechanism, 8a ... Seal case, 8b ... First sleeve, 8b1 ... Locking groove, 8c ... First rotating ring (rotating ring) ), 8d: first fixed ring, 8e: first holder, 8f: second sleeve, 8g: second rotating ring, 8h: second fixed ring, 8i: second holder, 8j ... 3rd rotation ring, 8k ... 3rd fixed ring, 8l ... 3rd holder, 9 ... collection | recovery apparatus, 10 ... nitrogen supply apparatus, 11 ... rotation ring position control nut (rotation ring position control member), 11a ...... Large-diameter portion, 11b ....... Extended portion, 11c..Opening portion, 11d .... Groove, 11e .... Opening portion, 11f ... Female thread, 12 ... O-ring (gasket), 13 ... Anti-rotation washer, 13a ... Projection, 13b ... Tongue, 13c ... Central opening, X ... Corrosive gas (compressed fluid), Y …… Nitrogen gas

Claims (9)

An impeller that compresses the fluid to be compressed; a housing that houses the impeller; a shaft that is connected to the impeller inside the housing; and the shaft that is disposed around the shaft and along the shaft. A turbo compressor comprising a dry gas seal mechanism for preventing leakage of compressed fluid,
A rotating ring restricting member that is provided inside the housing and restricts movement of the rotating ring to the impeller side of the dry gas seal mechanism;
The rotating ring restricting member is formed of a material that covers the entire peripheral surface of the tip portion of the shaft located inside the casing and has higher corrosion resistance to the compressed fluid than the shaft. Turbo compressor.   The turbo compressor according to claim 1, wherein the rotating ring restricting member is an annular member that is screwed into a tip portion of the shaft. The impeller has a connecting portion connected to the shaft;
The rotating ring restricting member has an extending portion extending to the connecting portion of the impeller;
The turbo compressor according to claim 2, further comprising a gasket interposed between the extending portion and the connecting portion. The rotating ring restricting member has a large diameter portion that is provided closer to the rotating ring than the extending portion and has a larger diameter than the extending portion,
The turbo compressor according to claim 3, wherein the extending portion is thinner in a radial direction than the large diameter portion. An impeller that compresses a fluid to be compressed and a rotary ring provided in a dry gas seal mechanism that is screwed into a tip portion of a shaft that is connected inside the casing that houses the impeller and that is disposed around the shaft. A rotary ring position regulating nut for regulating movement toward the impeller side,
A rotating ring position regulating nut characterized by covering the entire peripheral surface of the tip portion of the shaft located inside the housing and being made of a material having higher corrosion resistance against the fluid to be compressed than the shaft. A housing,
A shaft provided inside the housing;
An impeller connected to the shaft;
A dry gas sealing mechanism provided inside the housing and including a rotating ring connected to the shaft;
The shaft is covered between the impeller and the dry gas seal mechanism, is fixed to the shaft in contact with the dry gas seal mechanism, and is formed of a material having higher corrosion resistance against corrosive gas than the shaft. A rotating ring regulating member;
Having a turbo compressor.   The turbo compressor according to claim 6, wherein the rotating ring restricting member is an annular member screwed into the shaft between the impeller and the dry gas seal mechanism. The rotary ring restricting member includes a first portion including a portion that contacts the dry gas seal mechanism, and a second portion that is between the first portion and the impeller and has a smaller diameter than the first portion. Item 8. The turbo compressor according to Item 7.   The turbo compressor according to claim 6, further comprising a rotation prevention washer provided between the rotation ring regulating member and the dry gas seal mechanism.

Images