JP2014088802A - Rotary machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a seal device and a rotary machine capable of preventing fluid leakage from between a head member and a casing by regulating the displacement of the head member without increasing the casing in size.SOLUTION: The rotary machine comprises: a cylindrical casing 5; a rotation shaft 2 and an impeller 3 that are disposed inside the casing 5; a stationary member 6 inserted into the interior of the casing 5 and forming a fluid passage in between the rotation shaft 2 and the impeller 3; a head member 50 disposed at the end of the stationary member 6 in an axial direction and regulating the movement of the stationary member 6 toward the end in the axial direction of the stationary member 6; and a regulating member 53 supported to an inner peripheral surface 5a of the casing 5 and regulating the displacement of the head member 50 toward the end thereof in the axial direction by an abutment on the head member 50 in the axial direction. The head member 50 comprises: a regulated part 55 regulated by the regulating member 53; and a part 59 to be pressed with an outer diameter smaller than that of the regulated part 55 disposed closer than the regulated part 55 to the axial direction center side to face the stationary member 6.

Description

  The present invention relates to a rotating machine.

For example, a rotary machine such as a compressor or a pump has a contact type leakage prevention mechanism such as a mechanical seal that prevents fluid from leaking to the outside of the casing because the internal pressure of the casing rises due to the rotation of the rotating shaft. May be provided.
In such a leakage prevention mechanism of a rotating machine, due to dimensional tolerance, pressure change, temperature change, etc., shaft tilt, casing deformation, etc. occur, and a gap is created in the seal part of the leakage prevention mechanism, causing fluid to flow. There was a risk of leakage.
Therefore, Patent Document 1 relates to a shaft seal device that seals between a rotating shaft and a stationary member arranged around the rotating shaft, even if the rotating shaft is tilted or shaken beyond an allowable range. A technique has been proposed in which the sealing performance can be maintained by following and moving.

By the way, in the rotary machine as described above, a stationary member such as a diaphragm that forms a fluid flow path in the casing is inserted into the casing and disposed outside in the radial direction of the rotating shaft. The stationary member tends to be displaced toward the end in the axial direction by a force in the thrust direction due to an increase in the internal pressure of the casing. Therefore, a support member called a head member is disposed on the axial end portion side of the stationary member, and the displacement in the axial end portion side of the stationary member is supported by supporting the force in the thrust direction by the support member. I try to regulate it.
In many cases, the head member is formed in a substantially annular shape with a rotary shaft, a bearing mechanism, a gas seal mechanism, and the like arranged on the radially inner side thereof. A seal member such as an O-ring is disposed on the outer peripheral surface of the head member, and the seal member prevents fluid from leaking from between the outer peripheral surface of the head member and the inner peripheral surface of the casing.

JP 2008-33933 A

  Incidentally, there is a demand for further downsizing and higher output in the above-described rotating machine. If the pressure of the fluid discharged from the rotating machine is simply increased, the pressure in the thrust direction against the head member 150 increases as shown in FIG. 5, and the end of the casing 105 that supports the head member 150 is increased. The edge 105a may be bent so as to spread outward in the radial direction. When the casing 105 is bent in this way, the inner peripheral side of the head member 150 is deformed or displaced toward the axial end (left side in FIG. 5), and the outer peripheral surface 150 a of the head member is It will be displaced in the direction of peeling from the inner peripheral surface 105b. Then, the sealing function such as the sealing member 165 disposed between the head member 150 and the casing 105 cannot be maintained, and the high-pressure fluid inside the casing 105 may leak to the outside. On the other hand, it is conceivable to improve the strength of the casing 105 so that the casing 105 is not bent. However, if the thickness of the casing 105 is increased or a reinforcing rib is provided on the outer peripheral surface, the outer diameter of the casing 105 is increased. There is a problem that the rotating machine becomes larger and the size of the rotating machine becomes larger.

  The present invention has been made in view of the above circumstances, and can prevent a fluid leakage from between the head member and the casing by restricting the displacement of the head member without increasing the size of the casing. An apparatus and a rotating machine are provided.

In order to solve the above problems, the following configuration is adopted.
A rotating machine according to the present invention includes a cylindrical casing, a rotor disposed inside the casing, a stationary member that is inserted into the casing and forms a fluid flow path between the rotor, A head member that is disposed at an axial end of the stationary member and restricts movement of the stationary member toward the axial end, and is supported by an inner peripheral surface of the casing, and is axially connected to the head member. A regulating member that regulates the displacement of the head member toward the axial end by contacting the head member, and the head member is regulated by the regulating member, and more than the regulated portion. It is characterized by having a pressure-receiving portion that is arranged on the center side in the axial direction and whose outer diameter is smaller than that of the restricted portion and faces the stationary member.
With this configuration, the pressure receiving area of the head member on which the pressure in the thrust direction acts is reduced because the outer diameter of the pressure-receiving portion is smaller than the portion to be regulated that is regulated by the regulating member. Therefore, it is possible to reduce the moment of force that displaces the inner peripheral side of the head member toward the axial end portion. Further, since a space can be secured on the inner peripheral side of the restricted portion, for example, a rotor bearing mechanism, a gas seal mechanism, or the like can be arranged. Therefore, it is possible to prevent fluid leakage by regulating the displacement of the head member without increasing the size of the casing.

Furthermore, the rotary machine according to the present invention is the rotary machine described above, wherein the head member is locked in the radial direction with respect to the casing between the regulated portion of the head member and the facing surface of the stepped portion of the casing. There may be provided radial locking means.
With this configuration, even if the axial end edge of the casing is bent so as to spread outward in the radial direction, the head member is separated from the casing in the radial direction by the radial locking means. Therefore, it is possible to more reliably prevent the fluid from leaking through the outer peripheral surface of the head member with a simple configuration.

Furthermore, the rotary machine according to the present invention may further include a fastening member that fastens the restriction member to the casing from the outside of the casing.
With this configuration, it is possible to prevent the restricting member from being displaced radially inward from the casing, that is, in the peeling direction, and thus it is possible to prevent the head member from being displaced in the axial direction.

  According to the rotating machine according to the present invention, the displacement of the head member can be regulated without enlarging the casing, and fluid leakage from between the head member and the casing can be prevented.

It is sectional drawing which shows the structure of the centrifugal compressor in 1st embodiment of this invention. It is an expanded sectional view of the color member of the above-mentioned centrifugal compressor. It is an expanded sectional view of the head member of the above-mentioned centrifugal compressor. It is an expanded sectional view equivalent to FIG. 3 in 2nd embodiment of this invention. It is explanatory drawing which shows the displacement of a general head member.

Hereinafter, a centrifugal compressor 1 which is a rotating machine in a first embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a schematic sectional view showing a centrifugal compressor 1 according to a first embodiment of the present invention.
As shown in FIG. 1, the centrifugal compressor 1 in this embodiment is a multistage centrifugal compressor, and has a configuration including two sets of three-stage impeller groups 3A and 3B, for example.

  The centrifugal compressor 1 includes a rotating shaft (rotor) 2 that rotates around an axis O, an impeller 3 that is attached to the rotating shaft 2 and compresses a process gas (fluid) G using centrifugal force, and a rotating shaft 2. A casing 5 that is rotatably supported and a stationary member 6 made of a diaphragm or the like that forms a return flow path 4 that is disposed inside the casing 5 and flows the process gas G from the high pressure side to the low pressure side are mainly provided.

  The casing 5 is formed so as to form a substantially cylindrical outline, and the rotary shaft 2 is disposed so as to penetrate the center thereof. Journal bearings 11 are provided at the base (right side in the figure) and the end (left side in the figure) of the rotary shaft 2 in the axis O direction (axial direction), and the load in the thrust direction is provided at the end of the rotary shaft 2. Is provided with a thrust bearing 5b. The rotary shaft 2 is rotatably supported by the journal bearing 11 and the thrust bearing 5b.

  In the casing 5, suction ports 7 a and 7 b for sucking the process gas G from the radially outer side are provided on the center side in the axis O direction from the journal bearing 11. Further, the casing 5 is provided with discharge ports 8a and 8b on the center side in the axis O direction with respect to the suction ports 7a and 7b in order to discharge the process gas G radially outward. In addition, the stationary member 6 disposed inside the casing 5 is formed with an internal space 9a for communicating the suction port 7a and the discharge port 8a, and an internal space 9b for communicating the suction port 7b and the discharge port 8b. ing.

  A plurality of impellers 3 are accommodated in the internal spaces 9a and 9b. These impellers 3 constitute two sets of three-stage impeller groups 3A and three-stage impeller groups 3B in which the directions of the blades 3b are opposite to each other in the direction of the axis O of the rotary shaft 2. The three-stage impeller group 3A and the three-stage impeller group 3B are attached to the rotary shaft 2 with their back surfaces directed toward the center in the axis O direction.

  The impeller 3 is a so-called closed-type impeller, and has a substantially disk-like disk 3a that is gradually expanded in the direction of the axis O toward the discharge ports 8a and 8b, and is radially attached to the disk 3a. And a cover portion 3c attached so as to cover the tip side of the plurality of blades 3b in the circumferential direction. An open impeller that does not include the cover portion 3c may be used.

  The blade 3b of the impeller 3 constituting the three-stage impeller group 3A and the blade 3b of the impeller 3 constituting the three-stage impeller group 3B are formed symmetrically around the axis O of the rotating shaft 2, and the rotating shaft 2 Is rotated, the three-stage impeller group 3A and the three-stage impeller group 3B are compressed while flowing the process gas G from the suction ports 7a and 7b toward the discharge ports 8a and 8b, respectively. .

  The internal spaces 9 a and 9 b are provided with a return flow path 4. The return flow path 4 circulates the process gas G from the flow path outlet 3d on the radially outer side of the impeller 3 toward the flow path inlet 3e on the radially inner side of the adjacent impeller. The return flow path 4 has a diffuser part 12, a bend part 13, and a return part 14. The diffuser section 12 guides the process gas G compressed by the impeller 3 and discharged from the flow path outlet 3d of the impeller 3 to the radially outer side to the radially outer side.

  Here, the radially outer side of the diffuser portion 12 communicates with the return portion 14 via the bend portion 13, but is connected to the third-stage impeller 3 of the three-stage impeller group 3A and the three-stage impeller group 3B. In the portion, discharge ports 8a and 8b are formed instead of the return portion 14.

  The bend portion 13 is a curved flow path, and one end side is connected to the diffuser portion 12 and the other end side is connected to the return portion 14. The bend unit 13 reverses the direction of the process gas G flowing radially outward through the diffuser unit 12 so as to be directed radially inward, and sends the gas to the return unit 14. The return portion 14 is connected to the other end side of the bend portion 13 on the radially outer side, and is connected to the flow path inlet 3e of the impeller 3 on the radially inner side.

The centrifugal compressor 1 of this embodiment has the above-described configuration. Next, the basic operation of the centrifugal compressor 1 will be described.
First, in the three-stage impeller group 3A, the process gas G sucked from the suction port 7a is caused to flow into the return flow path 4, and the impeller 3, the diffuser part 12, the bend part 13, and the return part 14 are in this order. Compress while flowing from stage 3 to stage 3. Thereafter, the compressed process gas G flowing to the third-stage diffuser section 12 is discharged from the discharge port 8a. The process gas G discharged from the discharge port 8a is sent to the suction port 7b through a pipeline (not shown) connected from the discharge port 8a to the suction port 7b.

  Next, in the three-stage impeller group 3B, the process gas G sucked from the suction port 7b is caused to flow into the return flow path 4, and the impeller 3, the diffuser part 12, the bend part 13, and the return part 14 are arranged in this order. To further compress while flowing to the third stage. Thereafter, the process gas G compressed by flowing up to the third-stage diffuser section 12 is discharged from the discharge port 8b.

  By the way, as described above, inside the cylindrical casing 5 of the centrifugal compressor 1 in this embodiment, the return flow path 4 is provided between the rotating member 10 having the impeller 3 attached to the rotating shaft 2 and the impeller 3. And a stationary member 6 such as a diaphragm for forming the. The stationary member 6 and the rotating member 10 are inserted from the end side of the casing 5 in the direction of the axis O (left side in FIG. 1) toward the base side (right side in FIG. 1). Support parts 20 and 21 for supporting the rotating member 10 and the stationary member 6 in the direction of the axis O are provided on the part and the base part, respectively.

Next, the support structures 20 and 21 will be described.
As shown in FIGS. 1 and 2, the support structure 20 includes a reduced diameter portion 22 that protrudes radially inward from the inner peripheral surface 5 a of the casing 5 in which the stationary member 6 is disposed at the base portion of the casing 5. Yes. The reduced diameter portion 22 has a tubular shape extending in the axis O direction by connecting a pair of annular wall surfaces 23, 24 extending in the radial direction and the inner peripheral edges of the wall surfaces 23, 24 on the base side and the end side in the axis O direction. The inner peripheral surface 25 is provided. A collar member 26 that supports the stationary member 6 in the direction of the axis O is inserted inside the reduced diameter portion 22. The collar member 26 is disposed on the base side in the axis O direction and has a small diameter portion 27 having an outer diameter slightly smaller than the inner diameter of the reduced diameter portion 22, and the collar member 26 is disposed on the end side in the axis O direction from the small diameter portion 27. Is also provided with a large-diameter portion 28 having a relatively large diameter. The collar member 26 includes a wall surface 29 extending in the radial direction between the large-diameter portion 28 and the small-diameter portion 27, and the wall surface 29 abuts against the wall surface 23 on the end side in the axis O direction of the reduced-diameter portion 22. The displacement of the collar member 26 toward the base side in the direction of the axis O is regulated. In addition, the collar member 26 includes an inner peripheral surface 32 in which a plurality of ring-shaped grooves 31 that are arranged to face the outer peripheral surface 2 a of the rotating shaft 2 via the space 30 are formed.

  In the small diameter portion 27 of the collar member 26, an annular recess 34 for attaching the bearing unit 33 including the journal bearing 11 described above is formed on the inner peripheral surface 27 a on the base side in the axis O direction. The bearing unit 33 is fixed to the collar member 26 from the base side in the axis O direction by a fastening member (not shown) such as a bolt, for example. Further, two gas seal mechanisms 35 and 36 that are in contact with the outer peripheral surface 2 a of the rotating shaft 2 are attached to the collar member 26 on the end side in the axis O direction with respect to the bearing unit 33. These gas seal mechanisms 35 and 36 are spaced apart from each other in the direction of the axis O.

  Here, in the collar member 26 described above, gas for sealing is supplied to and exhausted from the space 30 between the gas seal mechanisms 35 and 36, the rotary shaft 2, and the inner peripheral surface 32 of the collar member 26. A plurality of gas passages 37 are formed, and the internal pressure of the space 30 is higher than the outside of the casing 5. As the internal pressure of the space 30 is increased in this way, the process gas G is prevented from leaking from the bearing unit 33 from the base in the axis O direction to the end. The gas passage 37 mainly includes one supply passage 37a and two exhaust passages 37b as a set of pipes. The reduced diameter portion 22 is formed with a main supply passage 37c that is routed in the radial direction and has an end connected to the supply passage 37a. The collar member 26 is routed in the direction of the axis O. A main exhaust passage 37d having an end connected to the exhaust passage 37b is formed. Referring to FIG. 1, a plurality of drain passages 39 for discharging the liquefied gas seal inside the collar member 26 and oil from the bearing unit 33 do not enter the space portion 30 at the lower portion of the collar member 26. Thus, a gas supply path 40 for supplying a gas for sealing to the gas seal mechanism 36 is also formed.

  In the collar member 26, ring-shaped seal members 38 are disposed on both sides in the direction of the axis O of the connecting portion between the main supply path 37c and the supply path 37a. These sealing members 38 prevent gas sealing gas and high-pressure process gas G in the casing 5 from leaking from between the collar member 26 and the casing 5.

  As shown in FIGS. 1 and 3, at the end of the casing 5, there is a small diameter portion 43 having an inner diameter equivalent to the inner peripheral surface 5 a of the casing 5 where the stationary member 6 is disposed, and the small diameter portion 43. Further, an enlarged diameter portion 44 having an inner diameter enlarged on the radially outer side is formed. The inner peripheral surfaces 43 a and 44 a of the small diameter portion 43 and the large diameter portion 44 are formed so as to extend in the direction of the axis O, and the edge of the small diameter portion 43 on the end side in the axis O direction and the diameter expansion portion 44. A step 45 is formed between the edge on the base side in the axis O direction. The step 45 in this embodiment is mainly composed of a wall surface 45a extending in the radial direction. In addition, an annular square groove 46 extending in the circumferential direction is formed at the approximate center in the axis O direction of the enlarged diameter portion 44.

  A head member 50 that restricts movement of the stationary member 6 toward the end in the axis O direction is attached to the end of the casing 5 described above on the inner peripheral side across the small diameter portion 43 and the large diameter portion 44. . The displacement of the head member 50 toward one end side in the axis O direction is restricted by a restriction member 53 including a shearing 51 and a retaining ring 52. The restricting member 53 is configured such that the shearing 51 is disposed on the base side in the direction of the axis O, and the retaining ring 52 is disposed on the end side. The shearing ring 51 and the retaining ring 52 are formed in the same shape in the longitudinal cross section in the radial direction. Further, the sum of the thickness dimensions of the shearing ring 51 and the retaining ring 52 in the direction of the axis O is based on the width dimension of the square groove 46 in the direction of the axis O so that the restricting member 53 can be inserted into the square groove 46. Is slightly smaller. That is, by inserting the regulating member 53 into the square groove 46, the displacement of the regulating member 53 in the axis O direction is regulated by the wall surface 46 a extending in the radial direction of the square groove 46. Here, in order to insert the regulating member 53 into the square groove 46, first, the shearing 51 is inserted into the square groove 46 and moved toward the base side in the direction of the axis O, and then the shearing 51 is moved in the direction of the axis O of the retaining ring 52. The shear ring 51 is inserted into the square groove 46 from the end side so as to be adjacent to the retaining ring 52.

  In the state where the restricting member 53 is inserted into the square groove 46, the inner peripheral portion 54 protrudes radially inward from the inner peripheral surface 44 a of the enlarged diameter portion 44. The inner peripheral portion 54 protruding inward in the radial direction of the regulating member 53 is in contact with the head member 50 in the axis O direction. Thereby, the displacement of the head member 50 toward the end in the direction of the axis O is controlled, and the shearing force input from the head member 50 can be released to the casing 5 via the shearing 51 and the retaining ring 52. It is possible. Here, although not shown, the regulating member 53 is divided into a plurality of pieces in the circumferential direction, and the divided pieces are arranged side by side in the circumferential direction to form a substantially annular shape. 50 can be supported on the entire circumference in the circumferential direction.

  The head member 50 includes a regulated portion 55 whose displacement toward the end in the axis O direction is regulated by the regulating member 53. The regulated portion 55 is formed such that the outer diameter of the outer peripheral surface 55 a is slightly smaller than the inner diameter of the inner peripheral surface 44 a of the enlarged diameter portion 44 of the casing 5 described above. Further, a cutout portion 56 is formed on the outer peripheral side of the regulated portion 55 on the end side in the axis O direction. The cutout portion 56 includes a wall surface 56a extending in the radial direction and a peripheral surface 56b extending in the axis O direction. The wall surface 56a extending in the radial direction abuts on the shearing 51 in the axis O direction and extends in the axis O direction. The extending peripheral surface 56b contacts the inner peripheral surface 51a of the shearing. That is, when the shearing 51 comes into contact with the wall surface 56a extending in the radial direction, the displacement of the head member 50 in the direction of the axis O is regulated, and the shearing in a state of being inserted into the square groove 46 by the peripheral surface 56b extending in the axis O direction. The displacement of 51 inward in the radial direction is restricted.

  The regulated portion 55 of the head member 50 is also formed with an inner notch 57 on the end side in the axial line O direction on the radially inner side. An outer peripheral portion 58a on the base side in the direction of the axis O of the bearing unit 58 including the thrust bearing 5b and the journal bearing 11 is fixed to the inner cutout portion 57.

  In the head member 50, a pressure-receiving portion 59 whose outer diameter is smaller than that of the restricted portion 55 is formed on the base side in the axis O direction (in other words, on the center side in the axis O direction) with respect to the restricted portion 55 described above. ing. The outer diameter 59 a of the pressure-receiving portion 59 is formed to be slightly smaller than the inner diameter of the small-diameter portion 43 of the casing 5. A wall surface 59b of the pressure-receiving portion 59 on the base side in the axis O direction is attached so as to contact the wall surface 6a on the end side in the axis O direction of the stationary member 6. In addition, the head member 50 includes an inner peripheral surface 60 in which a plurality of ring-shaped grooves 66 are formed on the outer peripheral surface 2 a of the rotating shaft 2 so as to face each other with a space 63 interposed therebetween.

  Two gas seal mechanisms 61 and 62 that are in contact with the outer peripheral surface 2 a of the rotating shaft 2 are attached to the head member 50 on the base side in the axis O direction from the bearing unit 58. These gas seal mechanisms 61 and 62 are spaced apart from each other in the direction of the axis O, similarly to the gas seal mechanisms 35 and 36 described above. Here, in the head member 50 described above, in the same manner as the collar member 26 described above, the space 63 between the two gas seal mechanisms 61 and 62, the rotary shaft 2, and the head member 50 is sealed. A gas passage 64 for supplying and exhausting gas is formed, so that the internal pressure of the space 63 is higher than the outside of the casing 5. As the internal pressure of the space portion 63 is increased in this way, the process gas G is prevented from leaking from the base portion side in the axis O direction with respect to the bearing unit 58.

  The gas passage 64 includes one supply passage 64a and two exhaust passages 64b as a set of pipelines. Further, the enlarged diameter portion 44 of the casing 5 is formed with a main supply path 64c that is wired in the radial direction and has an end connected to the supply path 64a. The head member 50 has an axis O direction. A main exhaust passage 64d is formed which is routed toward the end and connected to the exhaust passage 64b at its end. In the head member 50, ring-shaped seal members 65 are arranged on the outer peripheral surface 55a on both sides in the axis O direction of the connecting portion between the main supply passage 64c and the supply passage 64a, and on the outer peripheral surface 59a of the pressurized portion 59. In addition, the gas sealing gas and the high-pressure process gas G in the casing 5 are prevented from leaking to the outside from between the head member 50 and the casing 5. Similar to the collar member 26, a plurality of drain passages 67 for discharging the liquefied gas seal inside the head member 50 and oil from the bearing unit do not enter the space at the lower part of the head member 50. Further, a gas supply path 68 for supplying a sealing gas to the gas seal mechanisms 61 and 62 is also formed.

  In the regulated portion 55 of the head member 50, a concave portion 70 is formed on the wall surface 55b opposite to the wall surface 56a on the regulating member 53 side in the axis O direction. The recess 70 is formed in a substantially annular shape that is continuous over the entire circumference in the circumferential direction. On the other hand, on the wall surface (opposing surface) 45a of the stepped portion 45 of the casing 5 that faces the wall surface 55b of the regulated portion 55, a convex portion 71 that protrudes toward the head member 50 in the axis O direction is formed. The convex portion 71 has a substantially annular shape that continues around the entire circumference in the circumferential direction, and the convex portion 71 is immersed in the concave portion 70 of the regulated portion 55 in a state where the head member 50 is attached to the casing 5. The head member 50 is locked to the casing 5 in the radial direction. That is, the convex portion 71 and the concave portion 72 constitute the radial locking means of the present invention, and this configuration restricts the relative displacement in the shear direction between the wall surface 45a and the wall surface 55b. . In addition, the recessed part 70 and the convex part 71 are not restricted to substantially cyclic | annular form, For example, it forms so that it may distribute intermittently in the circumferential direction, or the displacement to the shear direction of the wall surface 45a and the wall surface 55b arises. It may be provided only at an easy place.

  Therefore, according to the centrifugal compressor 1 of the first embodiment described above, the outer diameter of the pressurized portion 59 is smaller than the regulated portion 55 regulated by the regulating member 53, so that the thrust direction is increased. Since the pressure receiving area of the head member 50 on which pressure acts can be reduced, the moment of the force for displacing the inner peripheral side of the head member 50 to the axial end side is reduced, so that the head member 50 moves relative to the casing 5. Thus, displacement in the peeling direction can be prevented. Furthermore, since a space can be secured on the inner peripheral side of the regulated portion 55 while reducing the pressure receiving area, a sufficient space for arranging the bearing unit 58 and the gas seal mechanism 62 of the rotary shaft 2 is secured. be able to. As a result, it is possible to prevent the process gas G from leaking by regulating the displacement of the head member 50 without increasing the size of the casing 5.

  Further, even if the force in the thrust direction by the stationary member 6 increases and the end portion of the casing 5 in the axis O direction is bent so as to spread radially outward, the concave portion 70 and the convex portion 71 cause the wall surface 45a to Since the relative displacement in the shear direction with respect to the wall surface 55b can be restricted, the relative displacement of the head member 50 in the peeling direction, which is radially inward, with respect to the casing 5 can be restricted. As a result, it is possible to more reliably prevent the process gas G from leaking to the outside through the outer peripheral surfaces 55a and 59a of the head member 50 with a simple configuration.

  Next, a rotating machine according to a second embodiment of the present invention will be described with reference to the drawings. Note that the rotary machine of the second embodiment is different from the centrifugal compressor 1 which is the rotary machine of the first embodiment described above only in the support structure of the shearing 51, and therefore the same parts are denoted by the same reference numerals. A description will be omitted as well as explanation.

  As shown in FIG. 4, a through hole 75 is formed in the casing 5 of the rotating machine in this embodiment from the radially outer surface 46 b of the square groove 46 toward the radially outer side. These through holes 75 are formed at predetermined intervals in the circumferential direction. Further, a bolt hole 51c is formed in the shearing 51 constituting the regulating member 53 at a position facing the through hole 75 of the outer peripheral surface 51b. Further, a bolt (fastening member) 76 is inserted into the through hole 75, and a radial end portion of the bolt 76 is screwed into the bolt hole 51c. That is, the shearing 51 is fastened to the casing 5 by the bolts 76 from the outside of the casing 5. The predetermined interval at which the through-holes 75 are formed corresponds to the number of shearing 51 divided in the circumferential direction.

  Therefore, according to the rotary machine of the second embodiment described above, it is possible to prevent the shearing 51 from being displaced from the casing 5 in the radial direction, that is, in the peeling direction by the bolts 76, so that the head member 50 is in the direction of the axis O. It is possible to more reliably prevent the displacement.

The present invention is not limited to the configuration of each of the above-described embodiments, and the design can be changed without departing from the gist thereof.
For example, in each of the above-described embodiments, the case where the concave portion 70 is formed on the wall surface 55b of the regulated portion 55 and the convex portion 71 is formed on the wall surface 45a of the casing 5 has been described, but the concave portion 70 is formed on the wall surface 45a of the casing 5. And the convex portion 71 may be formed on the wall surface 55b of the regulated portion 55. Moreover, although the convex part 71 and the recessed part 70 showed an example of the cross-sectional semicircle shape in the figure, when the wall surface 45a and the wall surface 55b were put together, these wall surfaces 45a and 55b are to the shear direction which is radial direction. The shape is not limited to a semicircular cross section as long as the relative displacement can be regulated.

  Furthermore, in each embodiment mentioned above, although the case where only one step part 45 was formed in the head member 50 and the casing 5 was demonstrated, you may form two or more step parts 45. FIG. In this case, the convex portion 71 and the concave portion 70 may be formed for each step portion 45, or the convex portion 71 and the concave portion 70 may be formed only in any one of the step portions 45.

  Moreover, in each embodiment mentioned above, although demonstrated as an example the multistage centrifugal compressor 1 which compresses the process gas G as a rotary machine, it is not restricted to a multistage type, Moreover, it is limited to the centrifugal compressor 1. It is not a thing. For example, it may be a rotating machine that supports a stationary body whose internal pressure is increased by the head member 50 from the axial end portion side. For various rotating machines such as a radial flow turbine and a centrifugal pump that compresses liquid. Is also applicable.

  In each of the above-described embodiments, the case where the gas supply / exhaust passages 64 are provided in the head member 50 and the bearing unit 58 is fixed has been described as an example. However, the gas supply / exhaust passages 64 are provided. It is also applicable to the head member 50 that is not fixed to the bearing unit 58.

  Further, in the second embodiment described above, an example in which the bolt 76 is used as the fastening member has been described. However, the bolt 76 may be any fastening member that can regulate the displacement of the regulating member 53 from the outside to the inside in the radial direction. It is not limited to.

2 Rotating shaft (rotor)
3 Impeller (rotor)
5 Casing 5a Inner peripheral surface 6 Stationary member 45 Step part 45a Wall surface (opposing surface)
50 Head member 53 Restricting member 55 Restricted portion 59 Pressed portion 70 Recessed portion (radial locking means)
71 Convex (radial locking means)
76 Bolt (fastening member)

Claims (3)

A cylindrical casing;
A rotor disposed inside the casing;
A stationary member inserted into the casing and forming a fluid flow path with the rotor;
A head member that is disposed at an axial end of the stationary member and restricts movement of the stationary member toward the axial end;
A regulating member that is supported by the inner peripheral surface of the casing and that abuts the head member in the axial direction to regulate the displacement of the head member toward the axial end,
The head member includes a regulated part that is regulated by the regulating member, and a regulated part that is arranged closer to the center in the axial direction than the regulated part and has an outer diameter smaller than the regulated part and faces the stationary member. A rotating machine comprising a pressure part.   2. The rotation according to claim 1, further comprising radial locking means for locking the head member in a radial direction with respect to the casing between a regulated portion of the head member and a facing surface of the stepped portion of the casing. machine.   The rotating machine according to claim 1, further comprising a fastening member that fastens the regulating member to the casing from the outside of the casing.

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