EP3557063B1 - Compresseur à vis - Google Patents

Compresseur à vis Download PDF

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Publication number
EP3557063B1
EP3557063B1 EP16923645.2A EP16923645A EP3557063B1 EP 3557063 B1 EP3557063 B1 EP 3557063B1 EP 16923645 A EP16923645 A EP 16923645A EP 3557063 B1 EP3557063 B1 EP 3557063B1
Authority
EP
European Patent Office
Prior art keywords
screw
discharge
rotor
distal end
tooth
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP16923645.2A
Other languages
German (de)
English (en)
Other versions
EP3557063A4 (fr
EP3557063A1 (fr
Inventor
Takeshi Ito
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP3557063A1 publication Critical patent/EP3557063A1/fr
Publication of EP3557063A4 publication Critical patent/EP3557063A4/fr
Application granted granted Critical
Publication of EP3557063B1 publication Critical patent/EP3557063B1/fr
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Anticipated expiration legal-status Critical

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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
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels

Definitions

  • the present invention relates to a screw compressor and, more particularly, to measures to prevent damage to a gate rotor.
  • a single screw compressor of Patent Literature 1 includes a screw rotor and disc-shaped two gate rotors.
  • the screw rotor has a plurality of screw grooves at its outer peripheral portion.
  • a plurality of tooth portions is disposed radially in each of the gate rotors.
  • the screw rotor is rotatably located inside a cylindrical wall.
  • the cylindrical wall is provided inside a casing of the compressor.
  • each of the gate rotors is formed such that the tooth portions extend through the cylindrical wall and mesh with the screw grooves.
  • the two gate rotors have axes perpendicular to an axis of the screw rotor, and are symmetrically arranged across the screw rotor.
  • Two compression chambers are defined inside the cylindrical wall by an inner periphery of the cylindrical wall, the screw grooves, and the tooth portions of the gate rotors.
  • the screw rotor rotates while, of a pair of circumferentially opposing lateral faces of any one of the tooth portions of each gate rotor, the suction-side lateral face located on a suction side in a state where the tooth portion is in mesh with the screw groove and a wall portion that defines the screw groove are in contact with each other.
  • the screw rotor rotates in the reverse direction because of a difference in pressure, i.e., high and low, of refrigerant.
  • the screw rotor rotates in the reverse direction, the screw rotor rotates while the discharge-side lateral face of the pair of lateral faces of any one of the tooth portions and the wall portion that defines the screw groove are in contact with each other. Damage or abrasion may occur in the gate rotors because of this reverse rotation.
  • US5129800A discloses a single screw positive displacement compressor mechanism employing shallow gate rotor tooth penetration of the main rotor for purposes of reducing internal leakage and consequent compressor inefficiencies, wherein an interrupted main rotor thread for purposes of insuring multiple gate rotor teeth meshing with the drive portion of the main rotor thread, thereby reducing gate rotor tooth flank loads in the compressor section of the device. Provision is also made for main rotor thread baffling between the main rotor chamber section and the mechanism inlet.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2013-136957
  • Patent Literature 1 is based on the fact that economizer ports for introducing refrigerant gas into compression chambers are provided, so the structure of Patent Literature 1 cannot be applied to a compressor with no economizer port.
  • the present invention has been attained taking the problem mentioned above into consideration, and an object thereof is to suppress damage on or abrasion of a gate rotor during reverse rotation of a screw rotor.
  • Embodiment 1 A screw compressor according to an embodiment of the present invention, hereinafter Embodiment 1, is defined in appended claim 1.
  • At least part of the region in which the distal end portion of each of the tooth portions of the gate rotor and the discharge-side wall portion forming the screw groove, with which the distal end portion of the tooth portion meshes, face each other during reverse rotation has a non-contact structure, so damage on or abrasion of the gate rotor can be suppressed.
  • a screw compressor according to Embodiment 1 will be described with reference to Fig. 1 to Fig. 6 .
  • the screw compressor is connected to a refrigeration circuit that operates a vapor compression refrigeration cycle by circulating refrigerant.
  • Fig. 1 is a schematic sectional view of the screw compressor according to Embodiment 1 of the present invention.
  • the right side is a suction side
  • the left side is a discharge side.
  • Fig. 2 is a perspective view showing a portion at which screw grooves of a screw rotor and tooth portions of gate rotors mesh with each other in the screw compressor according to Embodiment 1 of the present invention.
  • the upper right side indicates the suction side
  • the lower left side indicates the discharge side.
  • the solid arrow represents a rotation direction of a screw shaft, and the outline arrows represent how suction gas is sucked.
  • the screw compressor 1 according to Embodiment 1 is a single screw compressor.
  • Embodiment 1 will be described by way of an example of a single screw compressor of a type in which two gate rotors 7 are meshed with one screw rotor 5.
  • the screw compressor 1 includes a cylindrical casing 2, a motor 3, a screw shaft 4, the screw rotor 5, and other components.
  • the motor 3 is accommodated in the casing 2.
  • the screw shaft 4 is fixed to the motor 3, and is driven to rotate by the motor 3.
  • the screw rotor 5 is fixed to the screw shaft 4.
  • An end portion of the screw shaft 4, not fixed to the motor 3, is rotatably supported via a bearing 6.
  • the motor 3 is formed of a stator 3a and a motor rotor 3b.
  • the stator 3a is fixed in the casing 2 so as to be internally in contact the casing 2.
  • the motor rotor 3b is disposed radially inside the stator 3a.
  • the motor rotor 3b, as well as the screw rotor 5, is fixed to the screw shaft 4, and is disposed along the same axis as the screw rotor 5.
  • the screw rotor 5 has a cylindrical shape.
  • a plurality of screw grooves 5a is formed at an outer peripheral portion of the screw rotor 5.
  • the screw grooves 5a run spirally from one end of the screw rotor 5 toward the other end thereof.
  • One end side (right side in Fig. 1 ) of the screw rotor 5 is the suction side from which refrigerant gas is sucked, and the other end side (left side in Fig. 1 ) is the discharge side from which refrigerant gas is discharged.
  • the inside of the casing 2 is separated by a separation wall (not shown) into a suction pressure space and a discharge pressure space.
  • the suction pressure space is filled with low-pressure refrigerant gas.
  • the discharge pressure space is filled with high-pressure refrigerant gas.
  • One end side of the screw rotor 5 communicates with the suction pressure space, and the other end side communicates with the discharge pressure space.
  • the two gate rotors 7 are disposed on the sides of the screw rotor 5 so as to be symmetric across the screw shaft 4.
  • Each of the gate rotors 7 has a disc shape.
  • a plurality of tooth portions 7a is provided radially at an outer periphery of each gate rotor 7 along a circumferential direction.
  • Each gate rotor 7 is supported by a gate rotor support 8.
  • Each gate rotor 7 is disposed such that the tooth portions 7a are in mesh with the screw grooves 5a of the screw rotor 5.
  • Compression chambers 10 are spaces each surrounded by the screw groove 5a, the tooth portions 7a of the gate rotor 7, an inner periphery of the casing 2, and a slide valve 9.
  • the compression chambers 10 are filled with refrigerant gas sucked from the suction pressure space. Oil for lubricating the bearing 6 and sealing the compression chambers 10 is also introduced into the compression chambers 10.
  • slide valves 9 are disposed between the inner periphery of the casing 2 and the screw rotor 5.
  • Each of the slide valves 9 is provided so as to be slidable in the direction of the screw shaft 4 of the screw rotor 5 along the outer periphery of the screw rotor 5.
  • Each slide valve 9 has an opening port 9a.
  • Discharge ports 2a (see Fig. 3 , given later) are formed in the casing 2.
  • the discharge ports 2a communicate with a discharge chamber 11 formed inside the casing 2.
  • High-pressure refrigerant gas and oil filled in the compression chambers 10 pass through the opening ports 9a of the slide valves 9 and then discharged to the discharge chamber 11 via the discharge ports 2a.
  • Fig. 3 illustrates the operation of the screw compressor according to Embodiment 1 of the present invention.
  • the screw rotor 5 rotates with the rotation of the screw shaft 4.
  • the screw rotates in the forward direction.
  • the gate rotors 7 also rotate with the rotation of the screw rotor 5, and a suction stroke, a compression stroke, and a discharge stroke are repeated in each compression chamber 10.
  • a compression operation will be described focusing on the compression chamber 10 dotted in Fig. 3 .
  • Fig. 3(a) shows a state of the compression chamber 10 in the suction stroke.
  • the screw groove 5a in which the compression chamber 10 is formed is meshed with the tooth portion 7a of the gate rotor 7.
  • this tooth portion 7a relatively moves toward the terminal end of the screw groove 5a.
  • the gate rotor 7 rotates in the narrow outline arrow direction.
  • the compression chamber 10 in the suction stroke is expanded to have the largest volume, communicates with a suction-side space of the casing 2, and is filled with low-pressure refrigerant gas.
  • the compression chamber 10 communicates with the discharge port 2a, as shown in Fig. 3(c) .
  • high-pressure refrigerant gas compressed in the compression chamber is discharged via the opening port 9a of the slide valve 9 (not shown in Fig. 3 ) to the discharge chamber 11 through the discharge port 2a.
  • Refrigerant discharged to the discharge chamber 11 is discharged to the outside of the screw compressor 1.
  • the pressure in the compression chamber 10 gradually increases in order of (a), (b), and (c), and is high in (c).
  • the screw rotor 5 rotates in the reverse direction as described above because of a pressure difference between the low-pressure side and high-pressure side of the screw rotor 5.
  • the pressure in the compression chamber 10 is reduced to be lower than the suction-side pressure, and, when the gate rotor 7 has the existing configuration to which no improvement of the present invention is applied, the gate rotor 7 is damaged. This phenomenon will be described later with reference to Fig. 4 and Fig. 5 .
  • Fig. 4 illustrates a location of the tooth portion of the gate rotor relative to the screw groove during forward rotation of the screw rotor.
  • Fig. 5 illustrates a location of the tooth portion of the gate rotor relative to the screw groove during reverse rotation of the screw rotor.
  • Fig. 4 and Fig. 5 both show an expansion plan of one screw groove together with the tooth portion of the gate rotor, meshed with the screw groove.
  • the arrow in Fig. 4 indicates a moving direction during forward rotation of the screw rotor 5.
  • the arrow in Fig. 5 indicates a moving direction of the screw rotor 5 during reverse rotation.
  • the right side is the suction side
  • the left side is the discharge side.
  • the tooth portion 7a of the gate rotor 7 contacts a suction-side wall portion 5bb that is a wall portion on the suction side, of two wall portions 5b forming the screw groove 5a with which the tooth portion 7a meshes as shown in Fig. 2 and Fig. 4 . More specifically, a suction-side lateral face 7c of the tooth portion 7a contacts the suction-side wall portion 5bb.
  • the suction-side lateral face 7c is, of a pair of circumferentially opposing lateral faces of the tooth portion 7a, the lateral face on the suction side in a state where the tooth portion 7a is in mesh with the screw groove 5a.
  • the lateral face on the discharge side is referred to as the discharge-side lateral face 7b.
  • the discharge-side wall portion 5ba is referred to as discharge-side wall portion 5ba.
  • a pressing force acts on the gate rotor 7 in a direction opposing to that during operation, and the discharge-side lateral face 7b of the tooth portion 7a contacts the discharge-side wall portion 5ba as shown in Fig. 5 .
  • the portion represented by dotted line in Fig. 5 shows the shape of the tooth portion of existing technologies in which the width of the tooth portion 7a is set to the same width from the proximal portion to the distal end portion.
  • the solid line represents the tooth portion 7a of Embodiment 1.
  • the distal end portion 70 of the discharge-side lateral face 7b of the tooth portion 7a contacts the discharge-side wall portion 5ba for a longer period of time during reverse rotation than the center portion and proximal portion of the discharge-side lateral face 7b, so damage or abrasion easily occurs at the distal end portion 70.
  • the angle formed by the surface 7d of the tooth portion 7a and the suction-side lateral face 7c is an obtuse angle; whereas the angle formed by the surface 7d and the discharge-side lateral face 7b is an acute angle, that is, the discharge-side thickness of the tooth portion 7a is smaller.
  • the angle formed by the surface 7d and the discharge-side side-surface 7b is an acute angle only at the discharge-side distal end portion, not entire portion of the discharge side of the tooth portion 7a.
  • the angle formed by the surface 7d and the discharge-side lateral face 7b is an obtuse angle.
  • the fact that the thickness of the discharge-side distal end portion of the tooth portion 7a is smaller also causes the tooth portion 7a to be easily damaged.
  • the reason why the tooth portion 7a is formed such that the above-described angle is changed to an acute angle or an obtuse angle depending on a location is that the angle of tangent relative to the discharge-side wall portion 5b of the screw groove 5a approaches a right angle toward the discharge side.
  • Embodiment 1 to avoid damage on the gate rotor 7 before it happens, the following structure is employed.
  • Fig. 6 is a schematic enlarged view showing part of the screw compressor according to Embodiment 1 of the present invention.
  • each tooth portion 7a has a shape in which a corner portion formed by the discharge-side lateral face 7b and distal end face 7e of the existing tooth portion 7a as represented by dashed line in Fig. 5 is cut out.
  • the space 12 is uniform, and a space dimension is preferably set to, for example, 20 ⁇ m to 70 ⁇ m. This space 12 is constantly formed while the tooth portion 7a is in mesh with the screw groove 5a.
  • the tooth portion 7a moves toward the discharge-side wall portion 5ba of the screw rotor 5 and contacts the discharge-side wall portion 5ba as shown in Fig. 5 ; however, a portion that contacts the discharge-side wall portion 5ba is the center to proximal portion of the tooth portion 7a, and the distal end portion does not contact the discharge-side wall portion 5ba. Thus, damage on the distal end portion of each tooth portion 7a is suppressed.
  • the space 12 is provided between the discharge-side wall portion 5ba and the distal end portion of each of the tooth portions 7a of each gate rotor 7, so damage on and abrasion of the distal end portion of each tooth portion 7a of each gate rotor 7 during reverse rotation are suppressed.
  • a portion that contacts the discharge-side wall portion 5ba in the tooth portion 7a is the center portion to proximal portion of each tooth portion 7a.
  • each tooth portion 7a In the center to proximal portion of each tooth portion 7a, the angle formed by the suction-side lateral face 7c of the tooth portion 7a and the surface 7d is not an acute angle unlike the distal end portion but an obtuse angle, so the center to proximal portion has high strength.
  • damage on the gate rotors 7 is reduced, and deterioration of performance by aging is reduced.
  • each tooth portion 7a is obtained by just changing the distal end shape of each tooth portion of the existing configuration in which the facewidth is the same from the proximal portion to the distal end portion, so the space 12 is easily applicable to the existing products as well.
  • Embodiment 1 as a configuration to form a space between the distal end portion of each tooth portion 7a and the discharge-side wall portion 5ba, the distal end-side facewidth of each tooth portion 7a is smaller than the proximal end-side facewidth of the tooth portion 7a because the position of the distal end portion 7ba of the discharge-side lateral face 7b of each tooth portion 7a shifts toward the suction side.
  • Example 1 another mode different from that of Embodiment 1 will be described as a configuration to form a space between the distal end portion of each tooth portion 7a and the discharge-side wall portion 5ba.
  • differences from Embodiment 1 will be mainly described, and components not described in Example 1 are similar to those of Embodiment 1.
  • Fig. 7 is a schematic sectional view of an essential portion of a screw compressor according to Embodiment 2
  • Fig. 8 is an expansion plan of a groove bottom of each screw groove of the screw compressor according to Example 1.
  • Example 1 during reverse rotation, a region 5c facing the distal end portion of each tooth portion 7a in the discharge-side wall portion 5ba is located on the discharge side as compared to the other region, and a space 13 is formed between the distal end portion of each tooth portion 7a and the discharge-side wall portion 5ba.
  • the alternate long and two short dashed line represents the location of the discharge-side wall portion 5ba in the other region that does not form the space 13 in the discharge-side wall portion 5ba.
  • the region 5c is a region that lies in the groove direction (arrow direction in Fig. 8 ) of the screw groove 5a with a depth comparable to the thickness of the tooth portion 7a from the groove bottom within the discharge-side wall portion 5ba.
  • the length of the space 13 in the groove direction is at least a length by which the tooth portion 7a moves along the screw groove 5a by the time the tooth portion 7a separates from the screw groove 5a from a state where the tooth portion 7a meshes with the screw groove 5a during reverse rotation. This space 13 is always formed while the tooth portion 7a is in mesh with the screw groove 5a.
  • each space 13 is formed so as to extend in the groove direction of the screw groove 5a.
  • the length of each space 13 in the groove direction is made smaller than that of Example 1, and the location of the space 13 is restricted.
  • differences from Example 1 will be mainly described, and components not described in Example 2 are similar to those of Example 1.
  • Fig. 9 is a schematic sectional view of an essential portion of a screw compressor according to Example 2.
  • Fig. 10 is an expansion plan of a groove bottom of each screw groove of the screw compressor according to Example 2.
  • Example 2 part of a region facing the distal end portion of the tooth portion 7a in the discharge-side wall portion 5ba during reverse rotation, that is, part of a region that extends in the groove direction (arrow direction in Fig. 10 ), is located on the discharge side as compared to the other region and, as a result, the groove width widens toward the discharge side and increases.
  • the part is specifically an end region that is a distal end side in the rotation direction of the screw rotor 5 during reverse rotation within a region that extends in the groove direction (arrow direction in Fig. 10 ), that is, a region that communicates with the discharge port 2a (see Fig. 2 ).
  • Example 2 improves performance during normal operation as compared to Embodiment 1 and Example 1.
  • Example 2 advantageous effects similar to those of Example 1 are obtained, and additionally, since the location of the space 13 is restricted to the portion where damage on the tooth portion 7a can be suppressed more effectively than that of Example 1, that is, the region that communicates with the discharge port 2a, the following advantageous effect is obtained. That is, leakage of refrigerant through the space 13 during normal operation is suppressed as compared to those of Embodiment 1 and Example 1. Therefore, Example 2 improves performance during normal operation as compared to Embodiment 1 and Example 1.

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

Claims (3)

  1. Compresseur à vis (1) comprenant : un rotor de vis (5) comprenant une pluralité de rainures de vis (5a) sur une périphérie extérieure, une extrémité du rotor de vis étant un côté aspiration d'un fluide, une autre extrémité du rotor de vis étant un côté évacuation du fluide ; et deux rotors femelles (7) comprenant une pluralité de parties dents (7a) destinées à s'engrener avec la rainure de vis (5a) au niveau d'une partie périphérique extérieure, chacun des rotors femelles (7) tournant avec la rotation du rotor de vis (5) afin de comprimer le fluide, dans lequel :
    au cours d'une rotation inverse du rotor de vis (5), une partie au moins d'une région (5c) dans laquelle une partie extrémité distale de chacune des parties dents (7a), et une partie paroi du côté évacuation (5b) en tant que paroi du côté évacuation formant la rainure de vis (5a), avec laquelle s'engrène la partie extrémité distale de la partie dent (7a), se font face l'une à l'autre, présente une structure sans contact, où la structure sans contact est formée en tant qu'un espace (12) disposé entre la partie extrémité distale de chacune des parties dents (7a) et la partie paroi du côté évacuation (5b),
    le compresseur à vis (1) étant caractérisé en ce que : la largeur de denture de la partie extrémité distale de chacune des parties dents (7a), est inférieure à celle d'une autre partie de la partie dent (7a).
  2. Compresseur à vis (1) selon la revendication 1, dans lequel chacune des parties dents (7a) présente une forme dans laquelle est découpée une partie coin de la partie extrémité distale du côté évacuation.
  3. Compresseur à vis (1) selon la revendication 2, dans lequel l'espace (12) est uniforme et présente une dimension comprise entre 20 µm et 70 µm.
EP16923645.2A 2016-12-16 2016-12-16 Compresseur à vis Active EP3557063B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/087623 WO2018109939A1 (fr) 2016-12-16 2016-12-16 Compresseur à vis

Publications (3)

Publication Number Publication Date
EP3557063A1 EP3557063A1 (fr) 2019-10-23
EP3557063A4 EP3557063A4 (fr) 2019-11-27
EP3557063B1 true EP3557063B1 (fr) 2021-07-07

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EP16923645.2A Active EP3557063B1 (fr) 2016-12-16 2016-12-16 Compresseur à vis

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EP (1) EP3557063B1 (fr)
JP (1) JPWO2018109939A1 (fr)
CN (1) CN210127943U9 (fr)
WO (1) WO2018109939A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024134863A1 (fr) * 2022-12-23 2024-06-27 三菱電機株式会社 Compresseur à vis et dispositif à cycle de réfrigération

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5129800A (en) * 1991-07-17 1992-07-14 The United States Of America As Represented By The Secretary Of The Navy Single screw interrupted thread positive displacement mechanism
JP3840899B2 (ja) * 2001-01-05 2006-11-01 ダイキン工業株式会社 シングルスクリュー圧縮機
JP4412417B2 (ja) * 2007-12-07 2010-02-10 ダイキン工業株式会社 シングルスクリュー圧縮機
JP2013136957A (ja) 2011-12-28 2013-07-11 Daikin Industries Ltd スクリュー圧縮機
JP2014126028A (ja) * 2012-12-27 2014-07-07 Daikin Ind Ltd スクリュー圧縮機
JP6221777B2 (ja) * 2014-01-28 2017-11-01 オムロン株式会社 シリンダ錠
JP6301735B2 (ja) * 2014-05-26 2018-03-28 大豊工業株式会社 スラスト軸受
JP2016017438A (ja) * 2014-07-07 2016-02-01 ダイキン工業株式会社 シングルスクリュー圧縮機
JP2016020644A (ja) * 2014-07-14 2016-02-04 ダイキン工業株式会社 シングルスクリュー圧縮機
JP2016037150A (ja) * 2014-08-07 2016-03-22 株式会社Fts 燃料タンクのサブタンクの取付構造

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
JPWO2018109939A1 (ja) 2019-07-04
EP3557063A4 (fr) 2019-11-27
WO2018109939A1 (fr) 2018-06-21
CN210127943U (zh) 2020-03-06
EP3557063A1 (fr) 2019-10-23
CN210127943U9 (zh) 2020-04-17

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