WO2015029755A1 - Compresseur à vis - Google Patents

Compresseur à vis Download PDF

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Publication number
WO2015029755A1
WO2015029755A1 PCT/JP2014/071085 JP2014071085W WO2015029755A1 WO 2015029755 A1 WO2015029755 A1 WO 2015029755A1 JP 2014071085 W JP2014071085 W JP 2014071085W WO 2015029755 A1 WO2015029755 A1 WO 2015029755A1
Authority
WO
WIPO (PCT)
Prior art keywords
port
radial
intake
screw compressor
discharge
Prior art date
Application number
PCT/JP2014/071085
Other languages
English (en)
Japanese (ja)
Inventor
洋輔 福島
次橋　一樹
木村　康正
Original Assignee
株式会社神戸製鋼所
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社神戸製鋼所 filed Critical 株式会社神戸製鋼所
Publication of WO2015029755A1 publication Critical patent/WO2015029755A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet

Definitions

  • the present invention relates to a screw compressor.
  • an intake port and a discharge port are respectively provided on the radial side and the axial side with respect to the rotor.
  • the intake port and the discharge port on the radial side are for ensuring a sufficient opening area.
  • the radial intake port is used for rotor inspection.
  • the rotor is inspected by visually observing the rotor from the suction port through the radial intake port. Therefore, the radial intake port is provided at a position facing the suction port. Further, in order to reduce the flow path resistance during discharge, the radial discharge port is provided at a position facing the discharge port.
  • the radial intake port is provided at a position where it can be directly viewed from the intake port, there is a problem that the direct noise generated during compression leaks to the upstream side through the radial intake port.
  • the radial discharge port is provided at a position where the radial discharge port can be directly viewed from the discharge port, there is a problem that the direct sound of noise generated during compression leaks to the downstream side through the radial discharge port. For this reason, it is necessary to install a sound absorbing mechanism such as an intake duct or to take measures to reduce the radiated sound from the pipe connected to the screw compressor, resulting in an increase in cost.
  • An object of the present invention is to provide a screw compressor capable of reducing noise leaking to the outside through a radial side port while suppressing an increase in cost.
  • the screw compressor in the present invention is a screw compressor that compresses the fluid sucked from the suction port and discharges it from the discharge port, and a pair of rotors, a rotor chamber that houses the pair of rotors, and the suction port or the above
  • a sound insulating plate is provided between the port and the opening so as to cover the port so that the port cannot be directly viewed from the opening.
  • the sound insulating plate that covers the port is disposed between the port and the opening so that the port cannot be directly viewed from the opening.
  • the sound insulating plate By covering the port with the sound insulating plate, noise radiated from the port hits the sound insulating plate, so that the noise is prevented from going straight toward the opening.
  • the sound absorption mechanism and the radiated sound countermeasure can be made simpler than before, and the cost can be reduced.
  • the area and shape of the port are not changed, the performance of the screw compressor can be maintained.
  • the opening may be the suction port
  • the port may be an intake port that communicates the suction port with the rotor chamber. According to said structure, it can reduce that the direct sound of the noise which generate
  • the opening may be the discharge port, and the port may be a discharge port that communicates the discharge port with the rotor chamber. According to said structure, it can reduce that the direct sound of the noise which generate
  • the sound insulating plate may be supported by a support member inserted from the opening toward the port.
  • the work for supporting the sound insulating plate does not have to be performed near the port. This makes it easy to use a sound insulation board even when work near the port becomes difficult, such as when the positional relationship between the opening and the port changes and it becomes impossible to use the tool inserted from the opening near the port. Can be installed.
  • the port is an intake port, by removing the support member, the intake port is not covered with the sound insulating plate, so that the rotor can be suitably inspected through the intake port.
  • a sound absorbing mechanism may be provided on the port side of the sound insulating plate.
  • emitted from a port can be made small by providing a sound absorption mechanism in the port side of a sound insulation board. Thereby, the noise which leaks outside via a port can be reduced further.
  • the screw compressor of the present invention by covering the port with the sound insulating plate, it is possible to reduce leakage of direct noise generated during compression to the outside through the port. Therefore, since the sound absorption mechanism and the radiated sound countermeasure can be made simpler than before, noise leaking to the outside through the radial side port can be reduced while suppressing an increase in cost.
  • FIG. 2 is a cross-sectional view taken along the line II-II in FIG.
  • FIG. 3 is a sectional view taken along line III-III in FIG. 1. It is the side view which looked at the screw compressor from the central-axis direction of the suction inlet. It is a top view of an intake side shielding member. It is a side view of an intake side shielding member.
  • FIG. 5B is a cross-sectional view taken along the line VV in FIG. 5A showing the intake-side shielding member. It is the side view which looked at the screw compressor from the central-axis direction of the suction inlet. It is the side view which looked at the screw compressor from the central-axis direction of the discharge outlet.
  • FIG. 11 is a cross-sectional view taken along the line II-II in FIG. 1 in the second embodiment. It is the side view which looked at the screw compressor from the central-axis direction of the suction inlet. It is XI-XI sectional drawing of FIG. It is the side view which looked at the screw compressor from the central-axis direction of the suction inlet.
  • FIG. 13 is a sectional view taken along line XIII-XIII in FIG. 12.
  • the screw compressor 1 by 1st Embodiment of this invention has the cylindrical casing 2 as shown in FIG.
  • the casing 2 is provided with a suction port 3 that is an opening for sucking fluid such as air into the casing 2, and a discharge port 4 that is an opening for discharging a compressed fluid from the casing 2.
  • the portion of the casing 2 where the suction port 3 is provided is a flange portion 2a to which an upstream pipe (not shown) is connected.
  • the part in which the discharge port 4 in the casing 2 was provided becomes the flange part 2b to which the downstream piping which is not shown in figure is connected.
  • FIG. 2 which is a cross-sectional view taken along the line II-II of FIG. 1
  • a rotor chamber 5 is formed inside the casing 2, and a pair of meshing rotors 6, 7 are contained in the rotor chamber 5. Contained.
  • One of the pair of rotors 6 and 7 is rotated by a drive motor (not shown), and the other is driven to rotate.
  • a radial side intake port (port) 8 for communicating the rotor chamber 5 and the suction port 3 is formed on the radial side of the pair of rotors 6 and 7.
  • an axial side intake port (not shown) that allows the rotor chamber 5 and the suction port 3 to communicate with each other is formed on the axial side of the pair of rotors 6 and 7.
  • FIG. 3 which is a sectional view taken along line III-III in FIG. 1, the casing 2 has a radial discharge port (port) 9 for communicating the rotor chamber 5 and the discharge port 4 with a pair of rotors 6, 7 is formed on the radial side.
  • an axial discharge port (not shown) for communicating the rotor chamber 5 and the discharge port 4 is formed on the axial side of the pair of rotors 6 and 7.
  • the suction port 3 is on the radial side of the pair of rotors 6, 7, and the center axis D is at a position that obliquely intersects the continuous direction C of the pair of rotors 6, 7 Is provided.
  • the discharge port 4 is on the radial side of the pair of rotors 6 and 7, and the central axis E obliquely intersects the connecting direction C of the pair of rotors 6 and 7. In the position.
  • the position of the suction port 3 and the discharge port 4 is not limited to the position where the central axis obliquely intersects the continuous direction C, and may be a position orthogonal to the continuous direction C, for example.
  • the fluid whose flow rate is adjusted by an intake adjustment valve flows into the casing 2 through the upstream pipe connected to the flange portion 2a, and the radial intake port 8 and the axial intake air
  • the air is sucked into the rotor chamber 5 from the port.
  • the fluid sucked into the rotor chamber 5 is compressed by the rotation of the pair of rotors 6, 7, and then discharged from the radial side discharge port 9 and the axial side discharge port through the downstream side pipe connected to the flange portion 2 b. It is supplied to the outside through.
  • the radial-side intake port 8 is provided at a position facing the suction port 3. That is, the radial-side intake port 8 has such a configuration so that the pair of rotors 6 and 7 can be inspected by visually observing the pair of rotors 6 and 7 from the suction port 3 through the radial-side intake port 8. In the position.
  • the intake side sound insulation member 11 mentioned later is not shown in figure.
  • the radial side discharge port 9 is provided at a position facing the discharge port 4. That is, the radial discharge port 9 is provided at such a position in order to reduce the flow path resistance during discharge.
  • the screw compressor 1 of the present embodiment has an intake-side sound insulation member 11 attached to the flange portion 2a and a discharge-side sound insulation member 21 attached to the flange portion 2b.
  • the intake-side sound insulation member 11 includes a flange 12 having an opening 12a in the center, One end is connected to the opening end of the flange 12 and a pair of support members 13 are opposed to each other with the opening 12a interposed therebetween.
  • the intake-side sound insulation member 11 is formed of a steel plate having a thickness of about 5 mm.
  • Each of the pair of support members 13 is curved along the curved shape of the opening 12a, and the other end side is inclined.
  • the pair of support members 13 are inserted into the casing 2 from the suction port 3 (see FIG. 2). Further, the surface 12b of the flange 12 on the support member 13 side comes into contact with the upstream end surface of the flange portion 2a when the support member 13 is inserted into the casing 2 (see FIG. 2).
  • the intake-side sound insulation member 11 has an intake-side sound insulation plate (sound insulation plate) 14 fixed between the other ends of the pair of support members 13.
  • the intake-side sound insulating plate 14 is made of a steel plate or the like having a thickness of about 5 mm, and covers a part of the range that can be directly viewed from the opening 12a, as shown in FIG. 5A.
  • the intake-side sound insulation member 11 is attached to the flange portion 2a so that the support member 13 is inserted into the casing 2 from the suction port 3, as shown in FIG.
  • the opening 12 a of the flange 12 communicates with the suction port 3.
  • an intake-side sound insulation plate 14 supported by a pair of support members 13 is disposed between the radial-side intake port 8 and the suction port 3.
  • the radial-side intake port 8 is covered with the intake-side sound insulation plate 14 so that it cannot be viewed directly from the suction port 3.
  • FIG. 6 which is a side view of the screw compressor 1 viewed from the direction of the central axis D of the suction port 3, the suction side sound insulation plate 14 disposed between the radial side suction port 8 and the suction port 3 serves as a radial. Since the side intake port 8 is covered, the radial side intake port 8 cannot be directly viewed from the suction port 3. Thus, by covering the radial side intake port 8 with the intake side sound insulation board 14, the noise radiated from the radial side intake port 8 hits the intake side sound insulation board 14, so that the noise travels straight toward the inlet 3. Is inhibited. As a result, it is possible to reduce leakage of direct noise generated during compression to the upstream side through the radial intake port 8.
  • the intake-side sound insulation plate 14 by supporting the intake-side sound insulation plate 14 with a pair of support members 13 inserted from the suction port 3 toward the radial intake port 8, the work for supporting the intake-side sound insulation plate 14 is performed on the radial intake port. You don't have to go around 8. As a result, the positional relationship between the suction port 3 and the radial side intake port 8 changes, and the tool inserted from the suction port 3 cannot be used in the vicinity of the radial side intake port 8. Even when it becomes difficult to work on the intake side, the intake-side sound insulation plate 14 can be easily installed.
  • the radial intake port 8 is not covered with the intake-side sound insulation plate 14, so that the rotors 6 and 7 can be suitably inspected via the radial-side intake port 8.
  • the discharge-side sound insulation member 21 has the same configuration as the intake-side sound insulation member 11, and includes a flange 22, a pair of support members 23, and a discharge-side sound insulation plate (sound insulation plate) 24. As shown in FIG. 3, the discharge-side sound insulating member 21 is attached to the flange portion 2 b so that the support member 23 is inserted into the casing 2 from the discharge port 4. When the discharge-side sound insulation member 21 is attached to the flange portion 2 b, the opening 22 a of the flange 22 communicates with the discharge port 4. A discharge-side sound insulation plate 24 supported by the pair of support members 23 is disposed between the radial-side discharge port 9 and the discharge port 4. As a result, the radial-side discharge port 9 is covered with the discharge-side sound insulating plate 24 so that it cannot be viewed directly from the discharge port 4.
  • FIG. 7 which is a side view of the screw compressor 1 as viewed from the direction of the central axis E of the discharge port 4, a radial is provided by a discharge-side sound insulating plate 24 disposed between the radial-side discharge port 9 and the discharge port 4. Since the side discharge port 9 is covered, the radial side discharge port 9 cannot be directly viewed from the discharge port 4. Thus, by covering the radial-side discharge port 9 with the discharge-side sound insulating plate 24, noise radiated from the radial-side discharge port 9 hits the discharge-side sound insulating plate 24, so that the noise goes straight toward the discharge port 4. Is inhibited. Thereby, it is possible to reduce leakage of direct noise generated during compression to the downstream side through the radial discharge port 9.
  • the operation for supporting the discharge-side sound insulating plate 24 is performed on the radial-side discharge port.
  • the positional relationship between the discharge port 4 and the radial side discharge port 9 changes, and the tool inserted from the discharge port 4 cannot be used in the vicinity of the radial side discharge port 9.
  • the discharge-side sound insulating plate 24 can be easily installed.
  • the intake-side sound insulating plate 14 that covers the radial-side intake port 8 so that the radial-side intake port 8 cannot be directly viewed from the suction port 3 is provided with the radial-side intake air. It arrange
  • FIG. By covering the radial-side intake port 8 with the intake-side sound insulating plate 14, noise radiated from the radial-side intake port 8 collides with the intake-side sound insulating plate 14. The As a result, it is possible to reduce leakage of direct noise generated during compression to the upstream side through the radial intake port 8.
  • the sound absorption mechanism and the radiated sound countermeasure can be made simpler than before, and the cost can be reduced. Thereby, it is possible to reduce noise leaking to the upstream side via the radial-side intake port 8 while suppressing an increase in cost. Moreover, since the area and shape of the radial side intake port 8 are not changed, the performance of the screw compressor 1 can be maintained.
  • the work for supporting the intake-side sound insulation plate 14 is performed in the vicinity of the radial-side intake port 8 by supporting the intake-side sound insulation plate 14 with a support member 13 inserted from the suction port 3 toward the radial intake port 8. You don't have to. As a result, the positional relationship between the suction port 3 and the radial side intake port 8 changes, and the tool inserted from the suction port 3 cannot be used in the vicinity of the radial side intake port 8. Even when it becomes difficult to work on the intake side, the intake-side sound insulation plate 14 can be easily installed. Further, by removing the support member 13, the radial-side intake port 8 is not covered with the intake-side sound insulation plate 14, so that the inspection of the rotors 6, 7 can be suitably performed via the radial-side intake port 8.
  • a discharge-side sound insulation plate 24 that covers the radial-side discharge port 9 is disposed between the radial-side discharge port 9 and the discharge port 4 so that the radial-side discharge port 9 cannot be directly viewed from the discharge port 4.
  • noise radiated from the radial-side discharge port 9 collides with the discharge-side sound insulating plate 24, so that the noise is prevented from traveling straight toward the discharge port 4. The Thereby, it is possible to reduce leakage of direct noise generated during compression to the downstream side through the radial discharge port 9. Therefore, the sound absorption mechanism and the radiated sound countermeasure can be made simpler than before, and the cost can be reduced.
  • the discharge side sound insulating plate 24 by supporting the discharge side sound insulating plate 24 with the support member 23 inserted from the discharge port 4 toward the radial side discharge port 9, the work for supporting the discharge side sound insulating plate 24 is performed in the vicinity of the radial side discharge port 9. You don't have to. As a result, the positional relationship between the discharge port 4 and the radial side discharge port 9 changes, and the tool inserted from the discharge port 4 cannot be used in the vicinity of the radial side discharge port 9. Even in the case where it becomes difficult to work on the discharge side, the discharge-side sound insulating plate 24 can be easily installed.
  • the screw compressor 201 of the present embodiment is different from the screw compressor 1 of the first embodiment in that, as shown in FIG. 9 which is a sectional view taken along the line II-II in FIG.
  • the sound absorbing mechanism 217 is provided on the radial side intake port 8 side of the plate 214.
  • the flange 212 provided in the intake side sound insulation member 211 is in contact with the upstream end face of the flange portion 2a. Further, between the pair of support members 213 provided in the intake side sound insulation member 211, the intake side sound insulation plate 214 and the porous plate 215 are fixed in this order from the suction port 3 side to the radial side intake port 8 side. Has been. Here, unlike the support member 13 of the first embodiment, the pair of support members 213 are not inclined on the radial side intake port 8 side.
  • the intake-side sound insulating plate 214 is fixed in parallel to the flange 212, and the perforated plate 215 is parallel to the flange 212 at the end of the pair of support members 213 on the radial-side intake port 8 side. It is fixed to.
  • the perforated plate 215 has a large number of through holes.
  • the porous plate 215 is made of aluminum, has a plate thickness of 0.3 mm, and a through hole has a hole diameter of 0.5 mm.
  • the perforated plate 215 preferably has a through-hole diameter of 3 mm or less and an aperture ratio of 3% or less.
  • a space between the intake-side sound insulating plate 214 and the porous plate 215 is an air layer 216.
  • a sound absorbing mechanism 217 is configured by the intake side sound insulating plate 214, the perforated plate 215, and the air layer 216.
  • a porous material such as steel wool may be provided on the radial side intake port 8 side of the intake side sound insulating plate 214 to absorb sound. In this case, it is preferable to cover the porous material with a punching metal so that the porous material does not scatter and enter the rotor chamber 5.
  • a sound absorbing mechanism having the same configuration may be provided on the radial side discharge port 9 side of the discharge side sound insulating plate provided in the discharge side sound insulating member 221 attached to the flange portion 2b.
  • the noise radiated from the radial intake port 8 is provided by providing the sound absorbing mechanism 217 on the radial intake port 8 side of the intake side sound insulating plate 214. It can be made smaller. Thereby, the noise which leaks to an upstream side via the radial side intake port 8 can be reduced further.
  • the screw compressor 301 of the present embodiment is different from the screw compressor 1 of the first embodiment as shown in FIG. 10 which is a side view of the screw compressor 301 viewed from the direction of the central axis D of the suction port 3.
  • the intake-side sound insulation plate 314 has a shape similar to the opening shape of the radial-side intake port 8.
  • the intake-side sound insulating member 311 includes a flange 312 having an opening 12 a in the center, a support member 313 having one end connected to the opening end of the flange 312, And an intake-side sound insulation plate 314 that is cantilevered by a support member 313.
  • the intake-side sound insulation plate 314 has the same shape as the opening shape of the radial-side intake port 8 as viewed from the direction of the central axis D of the suction port 3.
  • the radial-side intake port 8 is configured so that the radial-side intake port 8 cannot be directly viewed from the intake port 3 by the intake-side sound insulation plate 314 disposed between the radial-side intake port 8 and the intake port 3. Covered. Therefore, the noise radiated from the radial-side intake port 8 is inhibited from going straight toward the suction port 3. As a result, it is possible to reduce leakage of direct noise generated during compression to the upstream side through the radial intake port 8.
  • FIG. 13 which is a cross-sectional view taken along the line XIII-XIII of FIG. 12, the intake-side sound insulation plate 414 is supported by legs 414a connected to the wall surface forming the rotor chamber 5, and the radial-side intake port 8 and the intake port 3 is arranged. Between the intake side sound insulating plate 414 and the radial side intake port 8, a flow path 418 through which fluid flows is formed.
  • the suction side sound insulating plate 414 disposed between the radial side intake port 8 and the suction port 3 removes the radial side intake port 8 from the suction port 3 except for a hole 414 b described later.
  • the radial intake port 8 is covered so that it cannot be directly viewed. Therefore, the noise radiated from the radial-side intake port 8 is inhibited from going straight toward the suction port 3. As a result, it is possible to reduce leakage of direct noise generated during compression to the upstream side through the radial intake port 8.
  • a hole 414b is provided in the intake side sound insulating plate 414.
  • the hole 414 b is provided at a position where the inside of the rotor chamber 5 can be directly viewed from the suction port 3. Therefore, the pair of rotors 6 and 7 can be inspected by visual inspection from the suction port 3.
  • the discharge-side sound insulation plate may be formed integrally with the casing 2.
  • the present invention is not limited to the configuration in which the intake-side sound insulation plate and the discharge-side sound insulation plate are provided, and may be configured in which only one of them is provided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention concerne un compresseur à vis qui présente une paire de rotors et un carter, le carter comprenant : une chambre de rotor pour recevoir la paire de rotors ; et un orifice pour connecter la chambre de rotor et une ouverture qui sert d'ouverture d'aspiration ou d'ouverture de décharge. Une plaque d'insonorisation est disposée entre l'orifice et l'ouverture de telle sorte que l'orifice ne soit pas directement visible à partir de l'ouverture, qui est disposée sur le côté radial de la paire de rotors.
PCT/JP2014/071085 2013-08-30 2014-08-08 Compresseur à vis WO2015029755A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013-179661 2013-08-30
JP2013179661A JP6100652B2 (ja) 2013-08-30 2013-08-30 スクリュ圧縮機

Publications (1)

Publication Number Publication Date
WO2015029755A1 true WO2015029755A1 (fr) 2015-03-05

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JP (1) JP6100652B2 (fr)
WO (1) WO2015029755A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5454309A (en) * 1977-10-07 1979-04-28 Hitachi Ltd Silencer for use in a displacement fluid machine
JPS59176490A (ja) * 1983-03-24 1984-10-05 Toyoda Autom Loom Works Ltd スクリユ−圧縮機
JPH07133774A (ja) * 1993-11-09 1995-05-23 Hitachi Ltd オイルフリースクリュー圧縮機
JPH11315784A (ja) * 1998-04-30 1999-11-16 Tochigi Fuji Ind Co Ltd 流体機械
JP2003120558A (ja) * 2001-10-12 2003-04-23 Nissan Motor Co Ltd スクリュ式流体機械
WO2003093649A1 (fr) * 2002-05-01 2003-11-13 City University Compresseur-extenseur a vis

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5454309A (en) * 1977-10-07 1979-04-28 Hitachi Ltd Silencer for use in a displacement fluid machine
JPS59176490A (ja) * 1983-03-24 1984-10-05 Toyoda Autom Loom Works Ltd スクリユ−圧縮機
JPH07133774A (ja) * 1993-11-09 1995-05-23 Hitachi Ltd オイルフリースクリュー圧縮機
JPH11315784A (ja) * 1998-04-30 1999-11-16 Tochigi Fuji Ind Co Ltd 流体機械
JP2003120558A (ja) * 2001-10-12 2003-04-23 Nissan Motor Co Ltd スクリュ式流体機械
WO2003093649A1 (fr) * 2002-05-01 2003-11-13 City University Compresseur-extenseur a vis

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JP6100652B2 (ja) 2017-03-22
JP2015048739A (ja) 2015-03-16

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