JP6276098B2 - Pressure vessel - Google Patents

Description

  The present invention relates to a pressure vessel used in a gas cooler or the like for cooling high-pressure gas.

  Conventionally, a pressure vessel (gas cooler) for cooling high-pressure gas is known. The pressure vessel may have a rectangular parallelepiped shape in order to effectively use the installation space. For example, Patent Document 1 discloses a compressor including a rectangular parallelepiped intercooler and a rectangular parallelepiped aftercooler. The intercooler is a pressure vessel for cooling the gas compressed by the first compressor. An aftercooler is a pressure vessel for cooling the gas further compressed by the second compressor after flowing out of the intercooler. The intercooler and the aftercooler are disposed in the package adjacent to each other.

JP2013-155617A

  The compressor described in Patent Document 1 has two rectangular parallelepiped pressure vessels (intercooler and aftercooler). Although these pressure vessels are arranged adjacent to each other, a space for arranging both pressure vessels is required in the package. Also, these pressure vessels need to be designed individually.

  An object of the present invention is to provide a pressure vessel capable of both a reduction in installation space and a simple design.

  As means for solving the above-mentioned problems, the present invention comprises a rectangular parallelepiped container main body capable of accommodating high-pressure gas, and a flat partition provided in the container main body, Provided is a pressure vessel connected to the container body so as to form a first chamber as an intercooler having a rectangular parallelepiped shape together with a container body and a second chamber as an aftercooler having a rectangular parallelepiped shape.

  In the present invention, the first rectangular parallelepiped chamber (intercooler) and the second rectangular chamber (aftercooler) are formed in the single container body by the partition wall, so that the two rectangular parallelepiped pressure vessels are adjacent to each other as in the prior art. The installation space is reduced compared with the case where it is arranged. Furthermore, the design of the pressure vessel is simplified as compared with the case where the two pressure vessels are individually designed as in the prior art.

  Specifically, the container body has a rectangular upper wall, a rectangular bottom wall facing the upper wall, and a rectangular cylindrical peripheral wall connecting the peripheral edge of the upper wall and the peripheral edge of the bottom wall. The peripheral wall is connected to the pair of first opposing walls and the pair of first opposing walls in a posture orthogonal to the upper wall and the bottom wall, and is orthogonal to the upper wall and the bottom wall. And a pair of second opposing walls facing each other in a posture orthogonal to the pair of first opposing walls, and the partition wall is an inner surface of the upper wall in a posture orthogonal to the upper wall and the bottom wall And connected to the inner surfaces of the pair of second opposing walls in a posture parallel to the pair of first opposing walls and orthogonal to the pair of second opposing walls. It is preferable.

  In this way, the chambers are arranged in the horizontal direction when the bottom wall is placed on a horizontal plane, which is advantageous when there is a restriction in the height direction on the installation space of the pressure vessel.

  In this case, it is preferable that the ratio of the width dimension of the second opposing wall in the direction orthogonal to the partition wall to the height dimension of the peripheral wall is 1.0 to 3.3.

  In this way, the maximum stress generated in the pressure vessel when the internal pressure acts on the pressure vessel due to the flow of high-pressure gas into the first chamber and the second chamber becomes relatively small. Specifically, when a high-pressure gas flows into each chamber of the pressure vessel, a load in a direction in which each of the walls expands outward acts on the upper wall, the bottom wall, and the peripheral wall. As a result, the greatest stress is generated at the boundary between the upper wall and the peripheral wall and at the boundary between the bottom wall and the peripheral wall. In this pressure vessel, when the ratio is smaller than 1.0, the area of the peripheral wall is relatively large with respect to the area of the top wall and the area of the bottom wall, so that the deformation amount to the outside of the peripheral wall is relatively Become bigger. If it does so, the stress which arises in the said boundary will become comparatively large. On the contrary, when the ratio is larger than 3.3, the area of the upper wall and the area of the bottom wall are relatively increased with respect to the area of the peripheral wall. It becomes relatively large. Also in this case, the stress generated at the boundary becomes relatively large. In this invention, since the said ratio is set to 1.0-3.3, the stress (maximum stress which arises in this pressure vessel) which arises in the said boundary is suppressed comparatively small. For this reason, it becomes possible to make the thickness of a pressure vessel small, and from this, the weight of a pressure vessel can be reduced.

  In this case, the ratio is preferably 1.75 to 2.2.

  In this way, the maximum stress generated at the boundary is further reduced, and thus the pressure vessel can be further reduced in weight.

  More specifically, the ratio is preferably 2.

  If it does in this way, the cross section in the plane parallel to a pair of 2nd opposing wall of a 1st chamber and a 2nd chamber will become both substantially square. In other words, when the ratio is 2, since a substantially uniform load acts on each wall, the maximum stress generated in the pressure vessel (stress generated at the boundary) is minimized. Therefore, the thickness of the pressure vessel can be reduced, and the weight of the pressure vessel can be reduced.

  Further, in the present invention, it further includes a support portion capable of supporting a heat exchanger for cooling the high-pressure gas in the first chamber and the second chamber, and the support portion is the pair of first opposing surfaces. It is preferable to have an outer support part projecting from the inner surface of the wall toward the partition wall and an inner support part projecting from the side surface of the partition wall toward the pair of first opposing walls.

  In this way, the heat exchanger is stably supported, and the pair of first opposing walls are reinforced. Specifically, since the outer support portion has a shape protruding from the inner surfaces of the pair of first opposing walls toward the partition wall, the section modulus of the cross section including the first opposing wall and the outer support portion is increased. Therefore, the first opposing wall is reinforced. In other words, the outer support portion has both a function of reinforcing the pair of first opposing walls and a function of supporting the heat exchanger.

  Specifically, the outer support portion has a shape extending from one end to the other end of the pair of first opposing walls along a direction parallel to the partition wall, and the inner support portion is the outer support. It is preferable to have a shape extending from one end of the partition wall to the other end along a direction parallel to the portion.

  If it does in this way, the said heat exchanger will be accommodated in each chamber only by sliding a heat exchanger along an outer side support part and an inner side support part. Furthermore, since the outer side support part has a shape extending from one end of the pair of first opposing walls to the other end, the pair of first opposing walls is further reinforced.

  Further, the outer support portion and the inner support portion have a shape capable of supporting the heat exchanger so that spaces are formed above and below the heat exchanger in a state where the heat exchanger is supported. Is preferred.

  In this way, the heat exchanger is supported by the outer support portion and the inner support portion, so that, for example, a high-pressure gas flow path is formed in each room from the space above the heat exchanger to the space below. The Therefore, the high-pressure gas is effectively cooled.

  As described above, according to the present invention, it is possible to provide a pressure vessel capable of both a reduction in installation space and a simple design.

It is a perspective view of the pressure vessel of one embodiment of the present invention. It is a cross-sectional perspective view of the pressure vessel of FIG. It is a cross-sectional perspective view of the state in which the heat exchanger was accommodated in the pressure vessel of FIG. It is the schematic of the compression apparatus provided with the pressure vessel of FIG. It is the graph which showed the relationship between the ratio of the width dimension with respect to the height dimension of a container main body, and the maximum stress.

  A preferred embodiment of the present invention will be described with reference to FIGS.

  As shown in FIGS. 1 to 3, the pressure vessel of the present embodiment includes a rectangular parallelepiped container main body 10 capable of storing high-pressure gas, a flat partition wall 50 provided in the container main body 10, and It has. The partition wall 50 is integrally formed with the container body 10. The partition wall 50 is provided in the container body 10 so as to divide the space in the container body 10 into two equal parts. Specifically, the partition wall 50 is provided in the container main body 10 so as to form a first chamber 10 a having a rectangular parallelepiped shape and a second chamber 10 b having a rectangular parallelepiped shape together with the container main body 10. The pressure vessel is formed by casting, for example.

  As shown in FIG. 4, the pressure vessel of the present embodiment is used in a compression apparatus including a first compressor 101 and a second compressor 102. Specifically, the first chamber 10a of this pressure vessel is used as an intercooler for cooling the high-pressure gas compressed by the first compressor 101. The second chamber 10b is used as an aftercooler for cooling the high-pressure gas further compressed by the second compressor 102 after flowing out of the first chamber 10a (intercooler). 1 to 3, the introduction part for introducing the high-pressure gas discharged from the compressor into the chambers 10 a and 10 b is shown, and the high-pressure gas is led out from the chambers 10 a and 10 b to the outside. Illustration of the derivation unit for doing so is omitted. Moreover, the 1st compressor 101 and the 2nd compressor 102 are connected to the motor 103 via the gear.

  Hereinafter, the pressure vessel of this embodiment will be described in detail.

  As shown in FIGS. 1 to 3, the container body 10 includes a rectangular upper wall 20, a rectangular bottom wall 30 facing the upper wall 20, and a square cylindrical peripheral wall 40. In the present embodiment, since the volume of the first chamber 10a that is an intercooler and the volume of the second chamber 10b that is an aftercooler are substantially equal, the internal pressure acting on the first chamber 10a is greater than the internal pressure acting on the first chamber 10a. The one that acts is higher. However, the wall thicknesses of the walls 20, 30, 40 are all set to be the same. Specifically, the thickness of each of the walls 20, 30, and 40 is set to have a rigidity that can withstand the internal pressure acting on the second chamber 10b.

  The upper wall 20 has a flat plate shape. In the present embodiment, the upper wall 20 is formed in a rectangular shape that is long in one direction. In the following description, the longitudinal direction of the upper wall 20 is the X-axis direction, the alignment direction of the upper wall 20 and the bottom wall 30 is the Z-axis direction, and the direction orthogonal to both the X-axis direction and the Z-axis direction is the direction. The Y-axis direction is assumed.

  The bottom wall 30 has a flat plate shape. The bottom wall 30 is formed in a rectangular shape that is long in one direction (X-axis direction).

  The peripheral wall 40 connects the peripheral edge of the upper wall 20 and the peripheral edge of the bottom wall 30. The boundary between the peripheral wall 40 and the upper wall 20 and the boundary between the peripheral wall 40 and the bottom wall 30 are curved so as to be convex outward. That is, each side and each vertex of the container body 10 are curved so as to be convex outward. In the present embodiment, the shape of the container body 10 is referred to as a rectangular parallelepiped shape.

  The peripheral wall 40 includes a peripheral wall body 42 that is integrally connected to the upper wall 20 and the bottom wall 30, and a lid wall 48 that can be attached to and detached from the peripheral wall body 42. FIG. 1 shows a state in which a part of the lid wall 48 is broken.

  The peripheral wall main body 42 includes a pair of flat first opposing walls 44 facing each other and a pair of flat second opposing walls 46 facing each other in a posture orthogonal to the first opposing walls 44. In the present embodiment, each first opposing wall 44 is formed in a rectangular shape that is long in the same direction (X-axis direction) as the longitudinal direction of the upper wall 20 and the bottom wall 30. Each second opposing wall 46 is formed in a rectangular shape that is long in a direction (Y-axis direction) orthogonal to the first opposing wall 44. Both ends of each second facing wall 46 in the width direction (Y-axis direction) are connected to the first facing wall 44, respectively. Each second opposing wall 46 has a first opening 46a and a second opening 46b that penetrate the second opposing wall 46 in the thickness direction (X-axis direction). Each opening 46a, 46b is provided adjacent to each other in the same direction (Y-axis direction) as the arrangement direction of the pair of first opposing walls 44.

  The lid wall 48 has a shape that closes the first opening 46a and the second opening 46b. The lid wall 48 is fastened to the second facing wall 46 by a fastener such as a bolt in a posture to close the first opening 46a and the second opening 46b.

  The partition wall 50 has a flat plate shape. The partition wall 50 is connected to the inner surface of the upper wall 20 and the inner surface of the bottom wall 30 in a posture orthogonal to the upper wall 20 and the bottom wall 30. The partition wall 50 is in a position parallel to the pair of first opposing walls 44 and perpendicular to the pair of second opposing walls 46, and between the first openings 46a and the second openings 46b in the second opposing walls 46. Connected to the inside. In the present embodiment, the partition wall 50 is formed in a rectangular shape that is long in the same direction (X-axis direction) as the longitudinal direction of the upper wall 20 and the bottom wall 30. The wall thickness of the partition wall 50 is set to be the same as the wall thickness of the container body 10. However, the wall thickness of the partition wall 50 may be set smaller than the wall thickness of the container body 10. The partition wall 50 forms a rectangular parallelepiped first chamber 10 a (intercooler) and a rectangular parallelepiped second chamber 10 b (aftercooler) in the container body 10.

  As shown in FIG. 3, the first chamber 10a and the second chamber 10b of the pressure vessel accommodate heat exchangers 70 for cooling the high-pressure gas flowing into the chambers 10a and 10b, respectively. The pressure vessel of this embodiment further includes a support portion 60 that supports the heat exchanger 70. Specifically, the support portion 60 includes an outer support portion 62 provided on the inner surfaces of the pair of first opposing walls 44 and an inner support portion 64 provided on the side surface of the partition wall 50. In the present embodiment, the outer support portion 62 is integrally formed with the pair of opposing walls 44, and the inner support portion 64 is integrally formed with the partition wall 50.

  The outer support portion 62 has a shape protruding from the inner surface of each first facing wall 44 toward the inner side (the partition wall 50 side). The outer support portion 62 has a shape extending along a direction parallel to the longitudinal direction (X-axis direction) of each first facing wall 44. In the present embodiment, the outer support portion 62 has a shape extending from one end to the other end in the longitudinal direction of each first opposing wall 44 in the direction orthogonal to the second opposing wall 46. The outer support portion 62 is connected to the inner surface of each first facing wall 44 at a position spaced from the bottom wall 30 toward the upper wall 20 (upward).

  The inner support portion 64 has a shape protruding from each side surface of the partition wall 50 toward the outer side (first opposing wall 44 side). The inner support part 64 has a shape extending along a direction parallel to the outer support part 62. In the present embodiment, the inner support portion 64 has a shape that extends from one end to the other end in the longitudinal direction of the partition wall 50 in a direction orthogonal to the second facing wall 46. The inner support portion 64 is connected to the side surface of the partition wall 50 at a position spaced from the bottom wall 30 to the upper wall 20 side (upward). In the present embodiment, the height position of the inner support portion 64 relative to the bottom wall 30 is set to be the same as that of the outer support portion 62. The protruding amount of the inner support portion 64 from the side surface of the partition wall 50 is larger than the protruding amount of the outer support portion 62 from the inner surface of the first facing wall 44.

  As shown in FIG. 3, the outer support portion 62 and the inner support portion 64 have the heat exchanger 70 so that spaces are formed above and below the heat exchanger 70 in a state where the heat exchanger 70 is supported. The shape can be supported.

  Next, a procedure for housing the heat exchanger 70 in each chamber 10a, 10b of the pressure vessel will be described.

  First, with the lid wall 48 removed, the heat exchanger 70 is slid along the longitudinal direction (X-axis direction) of the support portions 62 and 64 through the first openings 46a. . Thereby, the said heat exchanger 70 is accommodated in the 1st chamber 10a. Similarly, the heat exchanger 70 is accommodated in the second chamber 10b.

  Thereafter, the lid wall 48 is attached to the second opposing wall 46. Thereby, each chamber 10a, 10b is sealed in the state in which the heat exchanger 70 was accommodated in the 1st chamber 10a and the 2nd chamber 10b, respectively.

  As described above, in the present embodiment, the first chamber 10a (intercooler) and the second chamber 10b (aftercooler) having a rectangular parallelepiped shape are formed in the single container body 10 by the partition wall 50. Thus, the installation space is reduced as compared with the case where two rectangular parallelepiped pressure vessels are arranged adjacent to each other. Furthermore, the design of the pressure vessel is simplified as compared with the case where the two pressure vessels are individually designed as in the prior art.

  In the present embodiment, the heat exchanger 70 is stably supported, and the pair of first opposing walls 44 are reinforced. Specifically, since the outer support portion 62 has a shape protruding from the inner surfaces of the pair of first opposing walls 44 toward the partition wall 50, the section modulus of the cross section including the first opposing wall 44 and the outer support portion 62 is growing. Therefore, the first opposing wall 44 is reinforced. In other words, the outer support portion 62 has both a function of reinforcing the pair of first opposing walls 44 and a function of supporting the heat exchanger 70.

  In the present embodiment, the outer support portion 62 has a shape extending from one end of the pair of first opposing walls 44 along the direction parallel to the partition wall 50 to the other end. The partition 50 has a shape extending from one end to the other end along a direction parallel to the outer support portion 62. For this reason, the heat exchanger 70 is accommodated in each chamber 10a, 10b only by sliding the heat exchanger 70 along the outer side support part 62 and the inner side support part 64. FIG. Furthermore, the pair of first opposing walls 44 are further reinforced by the outer support portion 62.

  In the present embodiment, as shown in FIG. 3, the outer support portion 62 and the inner support portion 64 are formed with spaces above and below the heat exchanger 70 in a state in which the heat exchanger 70 is supported. Thus, the heat exchanger 70 can be supported. For this reason, when the heat exchanger 70 is supported by the outer support part 62 and the inner support part 64, for example, high-pressure gas flowing from the space above the heat exchanger 70 to the space below the heat exchanger 70 in each chamber 10a, 10b. A flow path is formed. Therefore, effective cooling of the high-pressure gas flowing into the chambers 10a and 10b is possible.

  When high-pressure gas flows into the chambers 10a and 10b of the pressure vessel, a load is applied to the upper wall 20, the bottom wall 30, and the peripheral wall 40 in a direction in which these walls expand outward. As a result, the greatest stress is generated at the boundary between the upper wall 20 and the peripheral wall 40 and at the boundary between the bottom wall 30 and the peripheral wall 40.

  Here, when the ratio W / H of the width dimension W (dimension in the Y-axis direction) of the container main body 10 to the height dimension H (dimension in the Z-axis direction) of the container main body 10 becomes smaller than 1.0, the upper wall 20 The area of the peripheral wall 40 is relatively larger than the area of the bottom wall 30 and the area of the bottom wall 30. For this reason, since the deformation amount to the outside of the peripheral wall 40 becomes relatively large, the stress generated at the boundary also becomes relatively large. Conversely, when the ratio W / H is greater than 3.3, the area of the upper wall 20 and the area of the bottom wall 30 are relatively larger than the area of the peripheral wall 40. For this reason, since the deformation amount to the outside of the top wall 20 and the bottom wall 30 becomes relatively large, the stress generated at the boundary also becomes relatively large.

  Therefore, in the present embodiment, the ratio W / H is set in the range of 1.0 to 3.3. In this way, the stress generated at the boundary (maximum stress generated in the pressure vessel) can be kept relatively small. For this reason, it becomes possible to make the thickness of a pressure vessel small, and from this, the weight of a pressure vessel can be reduced.

  Furthermore, the ratio W / H is more preferably set in a range of 1.75 to 2.5. In this way, since the stress generated at the boundary can be further reduced, the pressure vessel can be further reduced in weight.

  The ratio W / H is more preferably set to 2. If it does in this way, the cross section in the plane (YZ plane) parallel to a pair of 2nd opposing wall 46 of the 1st chamber 10a and the 2nd chamber 10b will become substantially square. In other words, when the ratio W / H is 2, since a substantially uniform load acts on each wall, the maximum stress generated in the pressure vessel (stress generated at the boundary) is minimized. Therefore, the thickness of the pressure vessel can be further reduced, and the weight of the pressure vessel can be further reduced.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above description of the embodiments but by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

  For example, in the above-described embodiment, an example in which the upper wall 20 and the bottom wall 30 are long rectangles in a direction parallel to the partition wall 50 (X-axis direction) is shown. It may be a rectangle that is long in the orthogonal direction (Y-axis direction).

  Next, the Example about the pressure vessel of this embodiment is described.

  The maximum stress generated in the pressure vessel when an internal pressure of 10 MPa was applied to the pressure vessel was analyzed in the range where the ratio W / H was 0.75 to 4.0. FIG. 5 shows the result. The place where the maximum stress was generated was the boundary between the upper wall 20 and the peripheral wall 40 and the boundary between the bottom wall 30 and the peripheral wall 40. In the present embodiment, the wall thickness of the container main body 10 and the partition wall 50 are all 27.5 mm.

  As shown in FIG. 5, when the ratio W / H is taken on the horizontal axis and the maximum stress is taken on the vertical axis, a downwardly convex curve is obtained. From FIG. 5, it was confirmed that the maximum stress is relatively small when the ratio W / H is set to 1.0 to 3.3. Specifically, in this embodiment, the maximum stress is 400 MPa or less when the ratio W / H is in the range of 1.0 to 3.3. For this reason, when FCD400 is used as the material of the present pressure vessel, the ratio W / H is particularly preferably set to 1.0 to 3.3. That is, since the tensile strength of the FDC 400 is 400 MPa, the maximum stress generated in the pressure vessel can be suppressed to 400 MPa or less of the tensile strength by setting the ratio W / H to 1.0 to 3.3. .

  Furthermore, it can be seen from FIG. 5 that the ratio W / H is more preferably set in the range of 1.75 to 2.5. In this range, the maximum stress generated in the pressure vessel is suppressed to 320 MPa or less. For this reason, each wall can be thinned, thereby reducing the weight of the pressure vessel.

  5 that the maximum stress is the minimum value of 314 MPa when the ratio W / H is 2.

DESCRIPTION OF SYMBOLS 10 Container main body 10a 1st chamber 10b 2nd chamber 20 Upper wall 30 Bottom wall 40 Perimeter wall 42 Perimeter wall main body 44 A pair of 1st opposing wall 46 A pair of 2nd opposing wall 48 Lid wall 50 Bulkhead 60 Support part 62 Outer support part 64 Inner side Support 70 Heat exchanger

Claims (7)

A rectangular parallelepiped container body capable of storing high-pressure gas;
A flat partition provided in the container body;
A support portion for supporting a heat exchanger for cooling the high-pressure gas in the container body ,
The partition is connected to the container body so as to form a first chamber as an intercooler having a rectangular parallelepiped shape together with the container body and a second chamber as an aftercooler having a rectangular parallelepiped shape ,
The container body has an upper wall, a bottom wall facing the upper wall, and a cylindrical peripheral wall connecting the peripheral edge of the upper wall and the peripheral edge of the bottom wall,
The peripheral wall is connected to the pair of first opposing walls and the pair of first opposing walls in a posture orthogonal to the upper wall and the bottom wall, and is orthogonal to the upper wall and the bottom wall. And a pair of second opposing walls facing each other,
The partition wall is connected to the inner surface of the upper wall and the inner surface of the bottom wall in a posture orthogonal to the upper wall and the bottom wall, and is in a posture parallel to the pair of first opposing walls. Connected to the inner surface of the second opposing wall,
The support portion includes an outer support portion projecting from the inner surface of the pair of first opposing walls toward the partition wall, and an inner support portion projecting from a side surface of the partition wall toward the pair of first opposing walls. Have
A pressure container in which a protruding amount of the inner support portion from the partition wall is larger than a protruding amount of the outer support portion from the pair of first opposing walls . The pressure vessel according to claim 1,
The first chamber is configured to accommodate a first gas having a first pressure as the high-pressure gas,
The said 2nd chamber is a pressure vessel comprised so that accommodation of the 2nd gas higher pressure than said 1st gas as said high pressure gas was possible . The pressure vessel according to claim 1 or 2 ,
The ratio of the width dimension of the direction orthogonal to the said partition of the said 2nd opposing wall with respect to the height dimension of the said surrounding wall is a pressure vessel which is 1.0-3.3. The pressure vessel according to claim 3,
The pressure vessel whose said ratio is 1.75-2.2. The pressure vessel according to claim 4,
A pressure vessel in which the ratio is 2. The pressure vessel according to any one of claims 1 to 5 ,
The outer support portion has a shape extending from one end to the other end of the pair of first opposing walls along a direction parallel to the partition wall,
The inner support portion is a pressure vessel having a shape extending from one end of the partition wall to the other end along a direction parallel to the outer support portion. The pressure vessel according to any one of claims 1 to 6 ,
The outer support portion and the inner support portion are pressure vessels having a shape capable of supporting the heat exchanger so that spaces are formed above and below the heat exchanger in a state where the heat exchanger is supported.

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