JP7059051B2 - Two-sided washer and rotary machine - Google Patents

Description

The present invention relates to a two-sided restraint washer and a rotary machine.

Conventionally, a compressor includes a rotor coupled to a rotating shaft, a bearing for supporting the rotating shaft, and a passenger compartment for accommodating the rotor. By rotating the rotor, gas is sucked into the passenger compartment from a suction port. Compress and discharge from the discharge port. As shown in Patent Document 1, for example, the passenger compartment of the compressor is divided in the horizontal direction, and the flange of the upper half-split body and the flange of the lower half-split body are fastened with bolts.
In Patent Document 1, the high-pressure gas inside the vehicle interior is prevented from leaking from between the flanges to the outside by engaging the grooves and protrusions formed on the mating surfaces of the flanges.

Japanese Patent No. 973814 (Japanese Patent Laid-Open No. 52-11704)

However, in a conventional compressor, high-pressure and high-temperature gas exists inside the passenger compartment, so that the pressure of the gas acts and thermal deformation occurs due to the temperature difference between the high-temperature gas and the bearing. Gas may leak due to deformation that opens the mouth of the mating surface between the flanges.
Even if grooves and protrusions are formed on the mating surfaces of the flanges as a leak prevention measure as in Patent Document 1, the gas leaks if the flange is deformed due to the pressure of the gas or the temperature gradient.

In order to prevent such gas leakage, the axial force (tightening force) of the bolt obtained by fastening is sufficiently dispersed not only in the vicinity of the bolt shaft but also around the shaft, thereby the mating surface of the flange. It is desirable that a predetermined surface pressure is secured over a wider range of.
Here, a washer is arranged between the head of the bolt, the nut attached to the bolt, and the flange. Since the range in which the tightening force is dispersed by the washer stays in a range close to the axis of one bolt in which the washer is arranged, the effect of preventing leakage is limited. If this washer is made thicker, the range in which the tightening force is dispersed is widened, but it is not sufficient to prevent leakage.

In addition, as another measure to prevent gas leakage, by thickening the flange, the effect of suppressing bending deformation of the flange and the effect of moving the opening starting point by expanding the bearing pressure range can be obtained, but the cost is obtained. There was a problem of increasing.

The present invention has been made in view of the above-mentioned problems, and is a two-sided restraint washer and a rotary machine capable of improving the sealing property between flanges by a low-cost structure and preventing fluid leakage. The purpose is to provide.

In order to achieve the above object, the two-sided restraint seat according to the present invention is provided with a tubular casing around which a fluid is introduced, and the casing is formed into a half-split body divided into two in the circumferential direction. , A two-sided restraint seat for fastening bolts that connect the flanges of each of the half-split bodies, and the outer peripheral curved surface of the half-split body faces in a direction away from the flange in the axial direction of the fastening bolt when viewed from the side. Gradually, a first contact surface that has a convex curved surface protruding from the outside of the casing and is in contact with the bearing surface of the flange, and a second contact surface that is in contact with the convex curved surface of the half-split body. The second contact surface is characterized in that it has a shape along the convex curved surface in a side view from a method orthogonal to the axial direction of the fastening bolt.

In order to achieve the above object, the rotary machine according to the present invention is characterized in that the flanges of the casing are joined to each other by the fastening bolts by using the two-sided restraint washer described above.

According to the present invention, when the pressure of the fluid in the casing increases, the convex curved surface of the casing pushed outward abuts on the second contact surface of the two-sided restraint washer. That is, since the casing is restrained from the outside by the second contact surface, it is possible to prevent the casing from being deformed to the outside. Therefore, the opening between the flanges can be suppressed to a small size, the sealing property between the flanges can be improved, and fluid leakage can be prevented.
Moreover, in the present invention, the structure is as simple as contacting the second contact surface of the two-sided restraint washer with the convex curved surface of the outer peripheral curved surface of the casing, so that the cost can be reduced.

Further, it is preferable that the two-sided restraint washer according to the present invention has a through hole through which a plurality of the fastening bolts can be inserted.

With such a configuration, one two-sided washer can share a plurality of fastening bolts, so that the range of dispersion of the fastening force on the bearing surface, including the area between adjacent fastening bolts, and the flange. Any of the dispersion ranges of the tightening force on the mating surface can be significantly expanded as compared with the case of the two-sided restraint washer corresponding to one fastening bolt. Moreover, since the number of washers can be reduced, the cost can be reduced.

Further, the two-sided restraint washer according to the present invention is characterized in that the second contact surface has a shape along the outer peripheral surface of the casing in a plan view seen from the axial direction of the fastening bolt. May be good.

According to such a configuration, the outer peripheral surface of the casing pushed outward can be brought into contact with the second contact surface of the two-sided restraint washer by surface contact. Therefore, the second contact surface can be more reliably restrained from the outside of the casing, and deformation to the outside (depth) of the casing can be prevented.

Further, in the rotary machine according to the present invention, it is preferable that the fastening bolt penetrates only one of the flanges and is screwed into the other flange, and the other flange is thicker than the one flange. ..

According to such a configuration, the height of the opening between the flanges can be suppressed to be smaller, and the second contact surface can be more reliably restrained from the outside of the casing, so that the outside (depth) of the casing can be restrained more reliably. ) Can be prevented.

Further, in the rotary machine according to the present invention, the fastening bolt penetrates both of the pair of flanges, and the two-sided restraint washer is provided between each nut portion at both ends of the bolt shaft portion and the flange. You may.

According to such a configuration, for example, a fastening bolt can be passed through the bolt, and a two-sided restraint washer can be applied to each of the pair of flanges. Therefore, the opening height can be reduced, and the amount of deformation to the outside (depth) of the casing can be suppressed to a small size.

According to the two-sided restraint washer and the rotary machine of the present invention, it is possible to prevent fluid leakage by improving the sealing property between the flanges.

It is a vertical sectional view which shows the structure of the centrifugal compressor by 1st Embodiment of this invention. It is a perspective view which shows the centrifugal compressor shown in FIG. It is a top view which shows the centrifugal compressor shown in FIG. It is a strange cross-sectional view which shows the state which connected the flanges with the implant bolt using the two-sided restraint washer. It is a schematic diagram which shows the distributed range of the tightening force of the implant bolt shown in FIG. FIG. 3 is a plan view of the implant bolt of FIG. 4 as viewed from above. It is a schematic diagram which shows the distributed range of the tightening force of a through bolt. It is a schematic diagram which shows the distributed range of the tightening force of the implant bolt by 2nd Embodiment. It is a schematic diagram which shows the distributed range of the tightening force of a through bolt by 1st modification. It is a plan view which shows the two-sided restraint washer by the 2nd modification, and is the figure which corresponds to FIG. It is a plan view which shows the two-sided restraint washer by the 3rd modification, and is the figure which corresponds to FIG. It is a plan view which shows the two-sided restraint washer by the 3rd modification, and is the figure which corresponds to FIG. It is a top view which shows the two-sided restraint washer by the 4th modification. It is a top view which shows the two-sided restraint washer by the 4th modification.

Hereinafter, the two-sided restraint washer and the rotary machine according to the embodiment of the present invention will be described with reference to the drawings. Such an embodiment shows one aspect of the present invention, does not limit the present invention, and can be arbitrarily changed within the scope of the technical idea of the present invention.

(First Embodiment)
As shown in FIG. 1, the two-sided restraint washer according to the present embodiment is applied to a centrifugal compressor 1 (rotary machine) provided with a vehicle interior 6 in which flanges are fastened to each other.

The centrifugal compressor 1 has a plurality of impellers 2 and is configured in a multi-stage system. The centrifugal compressor 1 is incorporated in plant equipment or the like, and compresses and discharges the process gas to be introduced.
The centrifugal compressor 1 is composed of a rotor 3 provided with a plurality of impellers 2, a diaphragm group 4, a sealing device 5, an upper half casing 20 (half-split body), and a lower half-chamber 30 (half-split body). It is provided with a vehicle compartment 6 (casing) configured.

The rotor 3 has a rotation shaft 3A extending in the horizontal direction and a plurality of impellers 2 coupled to the outer peripheral portion of the rotation shaft 3A. The axis of the rotation axis 3A is indicated by A, and the direction along the axis A is referred to as the axis direction D1. Both ends of the rotating shaft 3A are supported on the outside of the vehicle interior 6 by bearings (not shown).

As the rotary shaft 3A is rotated by a drive source such as a motor connected to the rotary shaft 3A, a plurality of impellers 2 are rotationally driven. Then, each impeller 2 compresses the process gas (working fluid) by centrifugal force.

The diaphragm group 4 is composed of a plurality of diaphragms 40 arranged along the axial direction D1 corresponding to each of the plurality of impellers 2. The diaphragm 40 is composed of members 40A and 40B connected via a return vane 40R.
The diaphragm group 4 covers the impeller 2 from the outer peripheral side.
The inner wall of the diaphragm 40 and the vehicle interior 6 defines a flow path that communicates with the flow path of the impeller 2 and allows the process gas to pass through.

The process gas sucked into the vehicle interior 6 from the suction port 11 by the rotation of the rotor 3 flows into the impeller 2 of the first stage through the suction flow path 12, and has a diameter from the outlet of the flow path of the impeller 2 by the diffuser flow path 13. It flows outward in the direction, passes through the curved flow path 14 and the return flow path 15, and flows into the inlet of the flow path located on the inner peripheral side of the impeller 2 in the next stage. Then, it repeatedly flows into the next-stage impeller 2 through the flow path of the impeller 2, the diffuser flow path 13, the curved flow path 14, and the return flow path 15, and the diffuser flow path 13 and the discharge from the final stage impeller 2 are repeated. It is discharged to the outside of the vehicle interior 6 through the discharge port 17 via the volute 16.

The discharge volute 16 is formed in an annular shape over the entire circumferential direction of the vehicle interior 6. The discharge volute 16 is formed so as to spread toward the inside (upstream side) of the axial direction D1 with respect to the position on the extension of the diffuser flow path 13 through which the high-pressure gas flowing out from the impeller 2 in the final stage flows. ..
In the present embodiment, the spreading direction of the discharge volute 16 is set to the inside of the axial direction D1, so that the rear end portion of the vehicle interior 6 is prevented from bulging toward the downstream side of the axial direction D1.
The rear end of the upper half passenger compartment 20 of the passenger compartment 6 has a pedestal 24 that is taller than the first flange 61 (see FIG. 2) of the upper half passenger compartment 20 and is behind the lower half passenger compartment 30. The end has a pedestal 34 that is taller than the second flange 62 (see FIG. 2) of the lower passenger compartment 30.

The sealing device 5 seals between the outer peripheral portion of the rotary shaft 3A and the vehicle interior 6 over the entire circumference to prevent the process gas from leaking to the outside of the vehicle interior 6. A labyrinth seal is suitable as the sealing device 5.
The sealing device 5 is arranged on both end sides of the rotating shaft 3A, and is held by the sealing housing holder 51. The outer peripheral portion of the seal housing holder 51 and the vehicle interior 6 are sealed by the seal member 52.

The vehicle interior 6 is formed in a substantially cylindrical shape, accommodates the rotor 3 and the diaphragm group 4 inside, and surrounds the outer peripheral portion of the seal housing holder 51.
The passenger compartment 6 can be formed from a metal material having corrosion resistance with respect to the process gas to be contacted. The vehicle interior 6 of the present embodiment is made of stainless steel.

The passenger compartment 6 includes an upper half passenger compartment 20 (FIGS. 1 to 3) and a lower half passenger compartment 30 (FIGS. 1 and 2) divided along a horizontal plane including the axis A. The upper half-cabin 20 and the lower half-chamber 30 are integrated by fastening the flanges 61 and 62, respectively.

As shown in FIGS. 1 and 3, the upper half-chamber 20 includes an accommodating portion 21 accommodating the rotor 3 and the diaphragm group 4, an enclosing portion 22 surrounding the seal housing holder 51, and the accommodating portion 21 and the enclosing portion 22. It is provided with a first flange 61 (one flange) protruding outward in the horizontal direction from the lower end of the housing.
The accommodating portion 21 has a semi-cylindrical peripheral wall 210, a front side wall 211 that closes the front end of the peripheral wall 210, and a rear side wall 212 that closes the rear end of the peripheral wall 210.
The surrounding portion 22 is formed in a semi-cylindrical shape having a diameter smaller than that of the accommodating portion 21, and is arranged on the front side (upstream side) of the accommodating portion 21 and the rear side (downstream side) of the accommodating portion 21, respectively. ..

The first flange 61 is arranged over the entire lower end of the accommodating portion 21 and the surrounding portion 22. The first flange 61 is formed with a large number of insertion holes 610 (see FIGS. 3 and 4) into which bolts are inserted. The insertion holes 610 are dispersedly arranged over the entire circumference of the first flange 61. Bolts 70 (see FIG. 1) used for fastening the upper half-chamber 20 and the lower half-chamber 30 are inserted into these insertion holes 610, respectively.

Of the insertion holes 620 near the rear end 6B of the vehicle interior 6 where the discharge port 17 is located, it is located on the innermost side (upstream side) of the axial direction D1 and is also the most rotating shaft in the radial direction D2b of the vehicle interior 6. A through bolt 70A (see FIG. 1) (fastening bolt) is used for the insertion hole 610X (see FIG. 3) located near 3A in order to resist the pressure of the gas compressed by the final stage. The through bolt 70A realizes the strengthening of the tightening force and the stress distribution over a wider range around the shaft as compared with the implant bolt 70B (see FIG. 1) (fastening bolt).
Implant bolts 70B may be used or through bolts 70A may be used for the other insertion holes 610.

Similarly to the upper half-chamber 20, the lower half-chamber 30 (see FIG. 1) also has the enclosing portion 32 surrounding the accommodating portion 31 and the seal housing holder 51, and horizontally from the lower ends of the accommodating portion 31 and the enclosing portion 32. A second flange 62 (the other flange) protruding outward is provided.
The second flange 62 of the lower half-chamber 30 is formed with a through hole through which a bolt is inserted or a female screw into which a bolt is screwed. Illustration of these through holes and female threads is omitted.

The upper surface of the second flange 62 of the lower half-chamber 30 and the lower surface of the first flange 61 of the upper half-chamber 20 are butted against each other. Hereinafter, the contact surface between the upper surface of the second flange 62 and the lower surface of the first flange 61 is referred to as a mating surface 612 of the first flange 61 and the second flange 62 (see FIGS. 3 and 4). The mating surface 612 of the first flange 61 is formed flat along the horizontal direction.

The through bolt 70A described above has a head portion 73 and a shaft portion 74 (see FIG. 7). With the lower surface of the first flange 61 and the upper surface of the second flange 62 abutting against each other, the shaft portion of the through bolt 70A has an insertion hole 610 (see FIG. 7) of the first flange 61 of the upper half-chamber 20. It penetrates through the insertion hole 610 of the second flange 62 of the lower half wheelchair 30. The shaft portion of the through bolt 70A protruding below the second flange 62 is screwed into the nut 71 (nut portion). A fastening member is composed of a through bolt 70A and a nut 71.

The above-mentioned implant bolt 70B (embedded bolt, stud bolt) has screws on both ends. The implant bolt 70B is inserted into the insertion hole 610 of the first flange 61 and the male screw of the second flange 62 of the lower half-chamber 30. The upper end of the implant bolt 70B is screwed into a nut 72 (nut portion) that functions as a bolt head (see FIGS. 4 and 5). The fastening member is composed of the implant bolt 70B and the nut 72.

It is assumed that the through bolt 70A, the implant bolt 70B, and the nuts 71 and 72 have a yield strength larger than the yield strength of the flanges 61 and 62.

When the axial force (tightening force) of the bolt 70 such as the through bolt 70A and the implant bolt 70B acts sufficiently, the first flange 61 and the second flange 62 are securely fastened with a sufficient tightening force.

During operation of the centrifugal compressor 1, the pressure of the gas inside the vehicle interior 6 creates an opening (gap) in the mating surface 612 of the first flange 61, and the gas leaks to the outside of the vehicle compartment 6 through the opening. Need to prevent. Further, the temperature difference between the upstream side and the downstream side in the vehicle compartment 6 due to the temperature rise due to the compression of the gas, particularly the temperature of the high-pressure gas near the rear end portion in the vehicle compartment 6, and the temperature of the high-pressure gas in the vehicle compartment 6 It is necessary to prevent the internal gas from leaking from the mating surface 612 due to thermal deformation of the flanges 61 and 62 due to the temperature difference with the bearing (not shown) located near the rear end portion.
In order to prevent leakage, in this embodiment, as shown in FIGS. 4 to 7, a two-sided washer 78 is used. In addition, in FIGS. 1 and 2, the two-sided restraint washer 78 is omitted.

As shown in FIGS. 4 and 5, a pair of flanges 61 and 62 are fastened by bolts 70 (implanted bolts 70B). A two-sided restraint washer 78 is arranged between the head of the bolt 70 (nut 72 (nut portion)) and the first flange 61. The tightening force of the bolt 70 is distributed from the nut 72 of the bolt 70 toward the first flange 61 via the two-sided washer 78 so as to spread in a conical shape around the axis of the bolt 70. Along with this, the tightening force is dispersed from the tip 70a of the shaft portion of the bolt 70 so as to spread in a conical shape opposite to the direction in which the nut 72 spreads. In FIG. 5, this dispersion range is indicated by reference numeral R.
As shown in FIG. 5, on the mating surface 612, the tightening force is dispersed over the dispersion range R. In the case of the implant bolt 70B, the maximum dispersion range in which the tightening force is distributed to the position farthest in the radial direction from the shaft is located between the seat surface 61a of the first flange 61 and the mating surface 612.

As shown in FIG. 7, also in the case of the through bolt 70A, the shape is conical around the axis of the through bolt 70A from the head 73 (nut portion) toward the first flange 61 via the two-sided restraint washer 78. The tightening force is dispersed so that it spreads. The tightening force is distributed vertically symmetrically from the nut 71 provided at the lower end of the through bolt 70A so as to spread in a conical shape in the opposite direction.
When the through bolt 70A is used, the shaft length is longer than that of the implant bolt 70B, so that the tightening force is distributed to a position radially farther from the shaft than the implant bolt 70B. Therefore, the dispersion range R in which the tightening force is dispersed on the mating surface 612 can be expanded as compared with the case where the implant bolt 70B is used.

In FIG. 7, the plate thicknesses of the flanges 61 and 62 are the same, and the fastening member composed of the through bolt 70A and the nut 71 and the flanges 61 and 62 are arranged line-symmetrically (vertically symmetrically) with respect to the mating surface 612. ing. Therefore, on the mating surface 612, the maximum dispersion range R in which the tightening force is dispersed to the position farthest in the radial direction from the shaft can be obtained.

As shown in FIGS. 4 to 7, the two-sided restraint washer 78 has a circular shape in a plan view, and has a first contact surface 78a that abuts on the seat surface 61a of the first flange 61 and an upper half casing 20. It has a second contact surface 78b that comes into contact with the outer peripheral curved surface 6a. The second contact surface 78b has a shape that coincides with the outer peripheral curved surface 6a in a side view from a method orthogonal to the axial direction of the bolt 70.

Next, the operation of the two-sided washer 78 and the centrifugal compressor 1 having the above-described configuration will be specifically described with reference to the drawings.
As shown in FIGS. 4, 5, and 7, in the present embodiment, when the pressure of the gas in the passenger compartment 6 becomes large, the passenger compartment 6 (upper half passenger compartment 20, lower) is pushed outward. The half-chamber 30) comes into contact with the second contact surface 78b of the two-sided restraint washer 78. That is, since the vehicle interior 6 is restrained from the outside by the second contact surface 78b, it is possible to prevent the vehicle interior 6 from being deformed to the outside. Therefore, the opening between the flanges 61 and 62 can be suppressed to a small size, the sealing property between the flanges 61 and 62 can be improved, and gas leakage can be prevented.
Moreover, in the present embodiment, the structure is as simple as the second contact surface 78b of the two-sided restraint washer 78 in contact with the outer peripheral curved surface 6a of the vehicle interior 6, so that the cost can be reduced.

Further, in the through bolt 70A of the present embodiment, both of the pair of flanges 61 and 62 are penetrated, and a two-sided restraint washer 78 is provided between the nut portions at both ends of the bolt shaft portion and the flanges 61 and 62. Therefore, it is possible to apply the two-sided restraint washer 78 to each of the pair of flanges 61 and 62. Therefore, the opening height can be reduced, and the amount of deformation to the outside (depth) of the vehicle interior 6 can be suppressed to a small size.

In the two-sided restraint washer and rotary machine according to the present embodiment described above, gas leakage can be prevented by improving the sealing property between the flanges 61 and 62.

Next, another embodiment and modification of the two-sided restraint washer and the rotary machine of the present invention will be described with reference to the accompanying drawings, but the same or similar members and parts as those of the above-described embodiment will be the same. The description is omitted by using reference numerals, and a configuration different from the embodiment will be described.

(Second embodiment)
As shown in FIG. 8, in the second embodiment, in the first embodiment described above, the thickness of the second flange 62 of the lower half-chamber 30 is the thickness of the first flange 61 of the upper half-chamber 20. It has a structure that is larger than the thickness.

In the second embodiment, the height of the opening between the flanges 61 and 62 can be suppressed to be smaller, and the second contact surface 78b can be more reliably restrained from the outside of the vehicle interior 6. Therefore, it is possible to prevent the vehicle interior 6 from being deformed to the outside (depth).

(First modification)
Further, in the first modification shown in FIG. 9, the heights of the nut portions (head 73, nut 71) located on both sides of the shaft portion of the through bolt 70A in the first embodiment described above are increased. Is.

In the case of the first modification, the surface contact between the outer peripheral curved surface 6a of the vehicle interior 6 pushed outward and the second contact surface 78b of the two-sided restraint washer 78 becomes large, so that the restraint effect is obtained even when the deformation is smaller. There is an advantage that can be exhibited.

(Second modification)
Further, in the second modification shown in FIG. 10, the plan view shape of the two-sided restraint washer 78A is a square shape (square shape in FIG. 10). As described above, the shape of the two-sided restraint washer 78 is formed along the outer peripheral curved surface 6a of the vehicle interior 6 in a side view from the viewpoint of the method in which the second contact surface 78b is orthogonal to the axial direction of the bolt 70. ..

(Third modification example)
Further, the two-sided restraint washers 78B and 78C according to the third modification shown in FIGS. 11 and 12 are formed with through holes through which a plurality of (here, two) bolts 70 can be inserted. FIG. 11 is a plan view shape of the two-sided restraint washer 78B, and both ends are curved surfaces. FIG. 12 shows a rectangular shape (rectangular shape) of the two-sided restraint washer 78C in a plan view.

In the third modification, the two-sided restraint washers 78B and 78C can be more reliably restrained from the outside of the vehicle interior 6 by the second contact surface 78b, and the deformation to the outside (depth) of the vehicle interior 6 is prevented. can do.

(Fourth modification)
Further, in the two-sided restraint washers 78 and 78D according to the fourth modification shown in FIGS. 13 and 14, the second contact surface 78b is viewed in a plan view from the axial direction of the bolt 70, and is along the outer peripheral curved surface 6a of the vehicle interior 6. It is curved in a shape. The two-sided restraint washer 78 shown in FIG. 14 is formed in a circular shape similar to the two-sided restraint washer 78 of the first embodiment described above, and coincides with the second contact surface 78b of the two-sided restraint washer 78. The outer peripheral curved surface 6a of the vehicle interior 6 is formed so as to do so.

In the fourth modification, the outer peripheral curved surface 6a of the vehicle interior 6 pushed outward can be brought into contact with the second contact surface 78b of the two-sided restraint washers 78 and 78D by surface contact. Therefore, the second contact surface 78b can be more reliably restrained from the outside of the vehicle interior 6, and deformation to the outside (depth) of the vehicle interior 6 can be prevented.

Although the embodiment of the two-sided washer and the rotary machine according to the present invention has been described above, the present invention is not limited to the above embodiment and can be appropriately changed without departing from the spirit of the present invention.

For example, in the present embodiment, the two-sided restraint washer 78 is provided on all the bolts 70 provided on the entire circumference of the flanges 61 and 62 of the vehicle interior 6, but the application is limited to all the bolts 70. Will not be done. For example, in the flanges 61 and 62, the two-sided washer 78 may be used only for the bolt 70 at the portion where the opening is large.

Further, in the two-sided restraint washers 78, 78A to 78D of the present embodiment, the shape of the second contact surface 78b is a shape that matches along the outer peripheral curved surface 6a of the vehicle interior 6, but they completely match. You are not limited to being there. For example, in a part of the circumferential direction facing the outer peripheral curved surface 6a of the vehicle interior 6, the diameter gradually increases from the outer peripheral edge of the first contact surface 78a toward the opposite surface side (upper side in FIG. 1) of the first contact surface 78a. The shape may be inclined so as to be outside the direction.

In addition, it is possible to appropriately replace the components in the above-described embodiments with well-known components without departing from the spirit of the present invention, and the above-described embodiments may be combined as appropriate.

1 Centrifugal compressor (rotary machine)
6 Car room (casing)
6a Outer curved surface 20 Upper half cabin (half split body)
30 Lower half car room (half split body)
61 First flange (one flange)
61a Seat surface 62 Second flange (the other flange)
70 bolt 70A through bolt (fastening bolt)
70B Implant bolt (fastening bolt)
71 Nut (nut part)
72 nut (nut part)
78 Two-sided restraint washer 78a First contact surface 78b Second contact surface 612 Combined surface R Dispersion range

Claims (6)

A fluid is introduced, and a cylindrical casing centered on the axis is provided. The casing is formed into a half-split body divided in the circumferential direction, and two surfaces of a fastening bolt for connecting the flanges of the half-split bodies to each other. It ’s a restraint washer,
The outer peripheral curved surface of the half-split body has a convex curved surface that gradually protrudes from the flange in the axial direction of the fastening bolt to the outside of the casing when viewed from the side surface.
A first contact surface that abuts on the bearing surface of the flange,
It has a second contact surface that contacts the convex curved surface of the half-split body, and has.
The second contact surface is a two-sided restraint washer having a shape along the convex curved surface when viewed from a side view from a method orthogonal to the axial direction of the fastening bolt. The two-sided restraint washer according to claim 1, wherein a through hole through which a plurality of the fastening bolts can be inserted is formed. The two-sided restraint washer according to claim 1 or 2, wherein the second contact surface has a shape along the outer peripheral surface of the casing in a plan view seen from the axial direction of the fastening bolt. A rotary machine in which the flanges of the casing are connected to each other by the fastening bolts using the two-sided restraint washer according to any one of claims 1 to 3. The fastening bolt penetrates only one of the flanges and is screwed into the other flange.
The rotary machine according to claim 4, wherein the other flange is thicker than the one flange. The fastening bolt penetrates both of the pair of flanges and
The rotary machine according to claim 4, wherein the two-sided restraint washer is provided between each nut portion at both ends of the bolt shaft portion and the flange.

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