JP2005325731A - High pressure screw compressor, and gas supply facility using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a high pressure screw compressor, in which strength of a casing is improved, and in which high pressure can be easily achieved in a device. <P>SOLUTION: This high pressure screw compressor 1 includes rotors 40, 50, and 60 in rotor chambers 13, 14, and 15 provided in the casing 10. The casing 10 comprises an inner drum 11 forming the rotor chambers 13, 14, and 15, and an outer drum 21 as a pressure-resistant casing. The inner drum 11 of complicated structure is formed of a casting. The outer drum 21 of simple structure is formed by forging. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a high-pressure screw compressor and a gas supply facility using the same.

  Conventionally, as shown in Patent Document 1, for example, a high-pressure screw compressor accommodates rotors in a plurality of rotor chambers provided in a casing, and sucks them from a suction port of a casing by simultaneously rotating the rotors. The gas is boosted in multiple stages by the plurality of rotors.

  In the conventional high-pressure screw compressor, since a complicated rotor chamber shape must be formed in the casing, it is necessary to use a cast product as a casing material constituting the pressure-resistant element.

  However, when a cast product is used as the casing material, there is a risk of causing a problem in strength such as a casting defect when it is desired to further increase the working pressure of the high-pressure screw compressor.

On the other hand, reciprocating type and diaphragm type compressors have been used for relatively small capacity and high pressure applications such as hydrogen supply stations. However, since these compressors are worn out, it is necessary to periodically replace sliding parts, valves, diaphragms, etc., and the maintenance thereof is complicated.
JP-A-4-36090

  The present invention has been made in view of the above points, and an object of the present invention is to provide a high-pressure screw compressor capable of easily improving the strength of the casing and easily increasing the pressure of the equipment, and a gas supply facility using the same. Is to provide.

  Another object of the present invention is to provide a high-pressure screw compressor that does not require periodic replacement of parts as a compressor used for small-capacity and high-pressure applications, and that can achieve a long life, and a gas supply facility using the same.

  The invention described in claim 1 is a high-pressure screw compressor in which a rotor is built in a rotor chamber provided in a casing, wherein the casing includes an inner cylinder forming the rotor chamber and an outer cylinder serving as a pressure-resistant casing. The high-pressure screw compressor is characterized in that it is configured.

  The invention according to claim 2 of the present application is the high-pressure screw compressor according to claim 1, wherein the outer body is formed by forging.

  The invention described in claim 3 of the present application is the high-pressure screw compressor according to claim 1 or 2, wherein the inner cylinder forming the rotor chamber has a horizontally divided shape.

  The invention according to claim 4 of the present application is a multi-stage high-pressure screw compressor in which the pressure is increased in multiple stages by incorporating a rotor in each of the plurality of rotor chambers, and the plurality of high-pressure screw compressors. 4. The high-pressure screw compressor according to claim 1, wherein the arrangement of the rotors and the gas pressure increase direction are opposed to each other.

  Invention of Claim 5 of this application exists in the gas supply equipment characterized by comprising using the high-pressure screw compressor of Claim 1, 2 or 3 or 4.

  According to the invention described in claim 1 of the present application, the inner cylinder in which a cast product must be used to form a rotor chamber having a complicated internal shape, and the outer cylinder that is a pressure-resistant element are separated into separate parts. Therefore, the material of the outer body, which is a pressure-resistant element, can be used with a stable and high strength such as a forged product if necessary, and therefore it is easy to increase the pressure of the equipment. it can.

  The rotor of the screw compressor is a male / female rotor, and both rotors are in rolling contact with each other. Therefore, wear does not occur and the service life is long. Thus, it is possible to extend the life of the compressor used in the above-described applications. And maintenance of gas supply equipment (Claim 5), gas pressurization equipment, refrigeration equipment, chemical plant equipment, etc. using this is also facilitated.

  According to the second aspect of the present invention, since the outer cylinder whose shape is not complicated is formed by forging, the strength can be stabilized and the strength can be increased, and high pressure can be easily coped with.

  According to the invention described in claim 3 of the present application, since the inner cylinder forming the rotor chamber is configured in a horizontally divided shape, the assembly and disassembly is facilitated, and the maintainability is improved.

  According to the invention described in claim 4 of the present application, since the arrangement of the plurality of rotors and the gas pressure increase direction are configured to face each other, the axial thrust due to the differential pressure generated between the suction side end surface and the discharge side end surface of each stage of the rotor Cancel each other out and the overall axial thrust can be reduced.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a schematic sectional view showing a high-pressure screw compressor 1 according to an embodiment of the present invention. As shown in the figure, the high-pressure screw compressor 1 is housed in a casing 10 composed of an inner cylinder 11 and an outer cylinder 21, and three rotor chambers 13, 14, 15 provided inside the inner cylinder 11, respectively. Three-stage rotors 40, 50, 60, a pair of shafts 70, 75 that are attached so that the three-stage rotors 40, 50, 60 rotate together, and one end of the shaft 70 is attached to rotate the shaft 70. The drive motor 80 to drive and the casing cover 100 attached to the end surface of the casing 10 opposite to the drive motor 80 are provided. Each component will be described below.

  The upper and lower parts of the inner cylinder 11 are configured in a horizontally split structure, and the two parts are joined and integrated to form a substantially cylindrical shape as a whole. In addition to the three rotor chambers 13, 14, 15, the inner cylinder 11 controls a complicated flow path (not shown) and a gas supply capacity to each of the rotor chambers 13, 14, 15. A slide valve storage space (not shown) is provided. In this way, the inner cylinder 11 having a complicated internal structure is constituted by a cast product. As described above, the inner cylinder 11 has a horizontally divided structure, which facilitates assembly and disassembly and improves maintainability.

  The outer cylinder 21 is a pressure-resistant component (pressure-resistant casing) that improves the pressure resistance of the high-pressure screw compressor 1, and is constituted by a forged product. That is, since the outer cylinder 21 is formed in a simple cylindrical shape that only surrounds the outer peripheral side surface of the inner cylinder 11, it can be constituted by a forged product.

  The inner cylinder 11 is housed in an outer cylinder 21 that is the pressure-resistant component. Further, since the pressure increase by the rotors 40, 50, 60 is generated as a differential pressure between the inner cylinder 11 / the outer cylinder 21, a gasket 25 is provided between the inner cylinder 11 / the outer cylinder 21, and is sealed.

  The casing 10 is connected to the discharge side of the rotor chamber 13 with a first-stage discharge port 27 and a second-stage suction port 29 (in the figure, they appear to overlap with each other), and the discharge side of the rotor chamber 14 has a second-stage discharge port. A discharge port 31 is connected, a third-stage suction port 33 is connected to the suction side of the rotor chamber 15, and a discharge port 35 is connected to the discharge side of the rotor chamber 15. The first stage outlet 27 and the second stage inlet 29 are connected to the intermediate cooler 37 by pipes 200 and 210, respectively. The second stage outlet 31 and the third stage inlet 33 are intermediately cooled by pipes 220 and 230, respectively. Connected to the device 39. Cooling oil injectors 240 and 250 are connected to the pipe 210 and the pipe 230, respectively.

  Each of the rotors 40, 50, 60 is constituted by a pair of male / female rotors, and either one of the male / female rotors is attached to one shaft 70, and the other is attached to the other shaft 75. The rotors 40, 50, 60 are engaged with each other while being in rolling contact with each other, and a differential pressure is generated between the suction side end face and the discharge side end face of each stage of the rotor 40, 50, 60 to increase the pressure. Further, when these rotors 40, 50, 60 are rotated in the same direction by the shafts 70, 75, the gas pressure increase direction by the rotors 40, 50, 60 is as shown by arrows in FIG. In this case, the rotor 60 faces away from the drive motor 80, and the rotor 60 faces the drive motor 80 side. That is, the arrangement of the rotors 40 and 50 and the gas pressure increasing direction are opposed to the arrangement of the rotor 60 and the gas pressure increasing direction.

  One end of the shaft 70 is a drive shaft of the drive motor 80, and the other end is pivotally supported by a bearing 71. Further, an interstage seal 73 is installed at a position between the rotor 50 and the rotor 60 of the shaft 70 so that the high-pressure third-stage discharge gas does not leak into the second-stage discharge portion having a low pressure.

  Further, both ends of the shaft 75 are supported by bearings 77 and 79, and an interstage seal 76 is installed at a position between the rotor 50 and the rotor 60, similarly to the shaft 70. The shaft 75 is a driven shaft, and rotates when the shaft 70 is driven to rotate.

  The drive motor 80 includes a rotor 81 attached to one end of the shaft 70, a stator 83 installed on the outer periphery of the rotor 81, and a motor casing 90 installed so as to surround the stator 83. Configured. A suction port 91 is provided in the center of one end surface of the motor casing 90 (surface opposite to the casing 10).

  When the drive motor 80 is driven, the rotors 40, 50, 60 are simultaneously rotated, whereby the gas sucked from the suction port 91 is first introduced into the rotor chamber 13 through the inside of the drive motor 80. Then, the first stage of pressure is increased by the rotor 40, and then the pressurized gas discharged from the rotor chamber 13 is cooled by the intermediate cooler 37 and then introduced into the rotor chamber 14, and the second stage of pressure is increased by the rotor 50. Further, the pressurized gas discharged from the rotor chamber 14 is cooled by the intermediate cooler 39 and then introduced into the rotor chamber 15, and the third pressure is increased by the rotor 60, and then discharged from the discharge port 35. The Gas cooling is also performed by appropriately injecting mist-like cooling oil into the pipes 210 and 230 from the two cooling oil injection devices 240 and 250.

  In the case of the high-pressure screw compressor 1 according to this embodiment, even if the internal pressure of the device is increased by the three-stage pressure increase, the outer cylinder 21 is constituted by a forged product, and its strength and reliability are improved. Because there is no problem.

  The high-pressure screw compressor 1 is driven by a pressure difference between the suction-side end face and the discharge-side end face of each stage of the rotors 40, 50, 60, thereby generating a large axial thrust. In the case of the screw compressor 1, the arrangement of the rotors 40 and 50 and the gas pressure increasing direction, and the arrangement of the rotor 60 and the gas pressure increasing direction are opposed to each other. Axial thrust can be reduced.

  In the above embodiment, the intermediate coolers 37 and 39 are installed between the stages of the rotors 40, 50, and 60. However, these intermediate coolers may be added or reduced as necessary. These intermediate coolers 37 and 39 may be omitted, and in that case, the rotor chambers 13, 14, 15 of each stage may be directly connected by a flow path provided in the inner cylinder 11. The installation positions of the cooling oil injection devices 240 and 250 can be variously changed, and the cooling oil injection devices 240 and 250 are not necessarily installed.

  FIG. 2 is an overall schematic configuration diagram of a gas supply facility configured using the high-pressure screw compressor 1 having the above structure. The gas supply facility shown in the figure is a gas supply facility for supplying hydrogen gas to the automobile 310, and stores a hydrogen dispenser unit 320 having a gas supply hose 321 to the automobile 310 and a hydrogen gas supplied to the hydrogen dispenser unit 320. And a compressor unit 340 having the high-pressure screw compressor 1 according to the present invention for supplying the pressurized gas to the pressure accumulator unit 330 or the hydrogen dispenser unit 320 under pressure. Yes. Open / close valves 351, 353, and 355 are attached to predetermined positions in the pipe 350 that connects the units. In order to store the hydrogen gas in the hydrogen trailer 360 in the accumulator unit 330, the hose 361 of the hydrogen trailer 360 is connected to one end of the pipe 350, the open / close valves 351 and 353 are closed, and the compressor unit 340 is driven. Then, the hydrogen gas increased in pressure is accumulated in the accumulator unit 330. On the other hand, when supplying hydrogen gas to the automobile 310 in the hydrogen dispenser unit 320, the open / close valve 351 is closed and the open / close valves 353 and 355 are opened, and hydrogen gas is supplied from the pressure accumulator unit 330 to the hydrogen dispenser unit 320.

  Needless to say, the high-pressure screw compressor 1 according to the present invention can be used in equipment for boosting various gases other than the gas supply equipment to high pressure, for example, gas pressurizing equipment for pressurizing various gases to high pressure, refrigerant gas, etc. It can be similarly used for other various facilities such as a refrigeration facility that pressurizes the gas to a high pressure and a chemical plant facility that pressurizes various gases for a chemical plant to a high pressure.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Is possible. Note that any shape, structure, or material not directly described in the specification and drawings is within the scope of the technical idea of the present invention as long as the effects and advantages of the present invention are exhibited. For example, in the above embodiment, the rotor chambers 13, 14, 15 housed in the high-pressure screw compressor 1 are increased in three stages, but the pressure is increased in one stage, two stages, or four or more stages. Also good. It goes without saying that various modifications can be made to the positions of the suction port 91 and the discharge port 35 and the shapes and structures of the components such as the inner cylinder 11 and the outer cylinder 21.

1 is a schematic cross-sectional view showing a high-pressure screw compressor 1 according to an embodiment of the present invention. 1 is an overall schematic configuration diagram of a gas supply facility configured using a high-pressure screw compressor 1. FIG.

Explanation of symbols

1 High-pressure screw compressor 10 Casing 11 Inner cylinder 13, 14, 15 Rotor chamber 21 Outer cylinder (pressure-resistant casing)
25 Gasket 35 Discharge port 37 Intermediate cooler 39 Intermediate cooler 40, 50, 60 Rotor 70 Shaft 71 Bearing 73 Interstage seal 75 Shaft 76 Interstage seal 77 Bearing 79 Bearing 80 Drive motor 90 Motor casing 91 Suction port 100 Casing cover 310 Automobile 320 Hydrogen dispenser unit 321 Gas supply hose 330 Pressure accumulator unit 340 Compressor unit 350 Piping 351, 353, 355 Open / close valve 360 Hydrogen trailer

Claims (5)

In the high-pressure screw compressor in which the rotor is built in the rotor chamber provided in the casing,
The high-pressure screw compressor is characterized in that the casing includes an inner cylinder forming the rotor chamber and an outer cylinder serving as a pressure-resistant casing.   The high pressure screw compressor according to claim 1, wherein the outer body is formed by forging.   3. The high-pressure screw compressor according to claim 1, wherein an inner cylinder forming the rotor chamber has a horizontally split shape.   The high-pressure screw compressor is a multi-stage high-pressure screw compressor that boosts the gas in multiple stages by incorporating a rotor in each of the plurality of rotor chambers, and the arrangement of the plurality of rotors and the gas pressurization direction are opposed to each other. The high-pressure screw compressor according to claim 1, 2 or 3, wherein the high-pressure screw compressor is configured in a shape.   A gas supply facility comprising the high-pressure screw compressor according to claim 1, 2, 3, or 4.

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