WO2002020992A1 - Compresseur helicoidal - Google Patents

Compresseur helicoidal Download PDF

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Publication number
WO2002020992A1
WO2002020992A1 PCT/JP2001/007613 JP0107613W WO0220992A1 WO 2002020992 A1 WO2002020992 A1 WO 2002020992A1 JP 0107613 W JP0107613 W JP 0107613W WO 0220992 A1 WO0220992 A1 WO 0220992A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller
helical
key groove
spiral groove
outer peripheral
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.)
Ceased
Application number
PCT/JP2001/007613
Other languages
English (en)
Japanese (ja)
Inventor
Takayoshi Fujiwara
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.)
Carrier Japan Corp
Original Assignee
Toshiba Carrier 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 Toshiba Carrier Corp filed Critical Toshiba Carrier Corp
Priority to AU2001282612A priority Critical patent/AU2001282612A1/en
Publication of WO2002020992A1 publication Critical patent/WO2002020992A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F04C18/10—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 internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member
    • F04C18/107—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 internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member with helical teeth

Definitions

  • the present invention relates to a helical compressor provided in a refrigeration cycle device, and more particularly to a helical compressor having an improved helical blade type compression mechanism roller structure.
  • refrigerators refrigeration / cooling showcases, air conditioners, and the like are equipped with a refrigeration cycle device, and this refrigeration cycle device incorporates a compressor that compresses refrigerant gas to increase the pressure.
  • Known compressors include reciprocating compressors and one-way compressors, as well as helical compressors using spiral blades.
  • the helical compressor accommodates an electric motor and a helical blade-type compression mechanism that is driven to rotate by the electric motor in a closed case.
  • the compression mechanism has a cylinder, a roller installed eccentrically in the cylinder, and a helical blade interposed between the porter and the cylinder.
  • the rollers of the compressor mechanism are driven by an electric motor and revolve within the cylinder. ⁇ Due to the revolving motion of the roller, the helical blade is moved into and out of the spiral groove of the roller, and the helical blade forms a plurality of compression chambers between the cylinder and the roller along the axial direction of the roller.
  • the plurality of compression chambers are formed so that the volume gradually decreases in the roller axis direction.
  • the volume of the compression chamber formed between the cylinder and the roller gradually and continuously increases while the roller revolves, and the compression chamber formed between the cylinder and the roller moves spirally in the axial direction of the roller.
  • the refrigerant gas is reduced, and the refrigerant gas is compressed, causing the high pressure to flow.
  • the axial length (total length) of the roller In order to prevent interference between the spiral groove formed on the outer peripheral surface of the roller and the key groove formed on the roller end surface, the axial length (total length) of the roller must be increased, and the overall length of the roller must be increased. If it is difficult, the keyway cannot be formed, making it difficult for the Oldham mechanism to smoothly and smoothly exhibit the rotation suppressing function, which may reduce compressor performance and reduce reliability. was there.
  • the present invention has been made in consideration of the above circumstances, and has a spiral groove and a key groove of an Oldham key that are efficiently arranged on a roller to reduce the size of the mouth.
  • the object is to provide a helical compressor with improved reliability.
  • Another object of the present invention is to provide a helical compressor in which the helical blade type compression mechanism can be made compact by making the rollers compact, and the compressor performance and reliability are improved. Disclosure of the invention
  • the present invention is a helical compressor having a closed case, an electric motor housed in one side of the closed case, and a helical blade type compression mechanism driven by the electric motor, wherein the helical blade type compression mechanism comprises: a cylinder; And a roller eccentrically arranged in the cylinder portion, and a helical blade interposed between the roller and the cylinder portion, and a spiral groove is formed on the outer peripheral surface of the roller.
  • the helical compressor characterized by being formed at a required side angle position.
  • the key groove when the suction end of the helical groove is set to 0 degree and the helical groove is formed in a positive circumferential direction, the key groove has a required angle in the negative circumferential direction. Formed in position. It is preferable that the key groove is formed within 90 degrees on the minus side in the circumferential direction, preferably in the range of minus 30 degrees to minus 60 degrees.
  • the roller has a pair of key grooves formed diametrically opposite the roller end face, and the key grooves are slidably engaged with the engaging teeth of the Oldham mechanism, and have a radial linear portion and a relief R. And formed from the part.
  • the roller outer peripheral shape of the key groove forming portion is provided so as to protrude from the remaining roller outer peripheral shape.
  • a refrigerant gas suction port is disposed between a required angle position on the key groove forming side on the minus side and approximately 0 degrees on the outer peripheral portion of the roller.
  • the refrigerant gas suction port is in a range of approximately 0 degrees on the outer peripheral portion of the roller to 120 degrees on the minus side on the key groove forming side.
  • a concave portion is formed in the outer peripheral portion of the roller over a required angle position on the side where the key groove is formed on the negative side from substantially 0 degree, and a concave relief portion is formed in the outer peripheral portion of the roller.
  • the roller has recesses for blade stoppers at both ends of the spiral groove. The both recesses are formed at the same angular position in the roller rotation direction.
  • a main bearing and a sub-bearing are provided, and the helical groove is formed at an irregular pitch from the sub-bearing toward the main bearing.
  • an Oldham mechanism that engages with the key groove may be provided between the mouthpiece and the sub bearing.
  • FIG. 1 is a longitudinal sectional view showing one embodiment of a helical compressor according to the present invention.
  • FIG. 2A and 2B are a front view and a cross-sectional view of a helical blade provided in the compression mechanism of the above-mentioned helical compressor.
  • FIG. 3A and FIG. 3B are a front view and a side view of a roller incorporated in the compression mechanism of the above-mentioned helical compressor.
  • 4A and 4B are a front view and a sectional view showing an Oldham ring for an Oldham mechanism provided in the compression mechanism of the helical compressor.
  • FIG. 5A shows the sub-equipment provided in the compression mechanism of the helical compressor.
  • FIG. 5B is a view showing the bearing, and
  • FIG. 5B is a cross-sectional view taken along the line VB-VB in FIG. 5A.
  • FIG. 6A and FIG. 6B are a front view and a side view showing a first modified example of the roller incorporated in the compression mechanism of the helical compressor according to the present invention.
  • 7A and 7B are a front view and a side view showing a second modification of the roller incorporated in the compression mechanism of the helical compressor according to the present invention.
  • FIG. 8A and FIG. 8B are a front view and a side view showing a third modification of the roller incorporated in the compression mechanism of the helical compressor according to the present invention.
  • 9A and 9B are a front view and a side view showing a fourth modification of the roller incorporated in the compression mechanism of the helical compressor according to the present invention.
  • FIG. 1 is a longitudinal sectional view showing a helical compressor according to the present invention.
  • the helical compressor 10 is incorporated into a refrigerating cycle of a refrigerator, a freezing showcase, a wine cooler, or the like.
  • the helical compressor 10 is a horizontal-type compressor employing spiral blades.
  • the horizontal helical compressor 10 includes an electric motor 12 housed on one side of a sealed case 11 and an electric motor 12 And a helical blade type compression mechanism 13 driven by.
  • the motor 1 2 is a stator 1 5 that is press-fitted and fixed to one side of the sealed case 11. And a mouth 16 accommodated in the station 15.
  • the electric motor 12 is driven by energization from the power supply terminal 17, and the rotor 16 is rotated.
  • the mouth 16 is rotatably mounted on the crank shaft 18 and fixed.
  • the crank shaft 18 is rotatably supported by a main bearing 20 and a sub bearing 21 provided in the compression mechanism 13.
  • the main bearing 20 supporting the crankshaft 18 has a boss protruding on both sides, and the sub-bearing 20 also has a boss protruding on one side.By increasing the axial length of each boss, The axial length of the bearing surface that rotatably supports the crankshaft 18 can be increased.
  • the crank shaft 18 is stably rotatably supported by the main bearing 21 and the sub-bearing 21.
  • the helical blade type compression mechanism 13 includes a sleep-shaped cylinder 23 housed and fixed in a sealed case 11, a roller 24 eccentrically arranged in the cylinder 23, and a roller 24.
  • a helical blade 25 interposed between the cylinder 23 and the helical blade 25;
  • outer peripheral flanges 23a and 23b are provided on the body, and the main bearing 20 and the sub-bearing 21 are mounted on these outer flanges 23a and 23b with tightening screws. Is fixed by the fastening means.
  • the roller 24 of the helical blade type compression mechanism 13 is rotatably mounted on the crank portion 18a of the crankshaft 18 so as to rotate eccentrically with the rotation of the crankshaft 18. ing.
  • An Oldham mechanism 27 is provided between the roller 24 and the sub bearing 21 to prevent the roller 24 from rotating (rotating).
  • the rotation (rotation) of the roller 2 is regulated by the Oldham mechanism 27, so that the roller 24 revolves without rotating inside the cylinder 22.
  • a spiral groove 28 is formed on the outer peripheral surface of the roller 24. This screw The spiral groove 28 is formed at an unequal pitch in which the groove pitch decreases from the sub-bearing 21 side to the main bearing 20 side.
  • the helical blade 25 is fitted into the spiral groove 28 of the roller 24. By the helical blade 25, a plurality of compression chambers 30 are formed between the cylinder 23 and the roller 24 along the axial direction.
  • the helical blade 25 is made of an injection moldable synthetic resin material, and has a rectangular cross section.
  • the helical blade 25 is made of fluororesin in consideration of blade characteristics such as flexibility, heat resistance, environmental resistance (refrigeration oil, temperature, and refrigerant), and low friction coefficient.
  • the cross section of the helical blade 25 is formed in a rectangular shape of side a X side b.
  • Fluororesin materials include perfluoroalkoxy resin materials (PFA resin materials), perfluoroethylene propylene (FEP) resin materials, ethylene tetrafluoroethylene (ETFE) resin materials, Chloroethylene (PCTFE) resin material.
  • a reinforcing material such as glass fiber or carbon fiber may be provided on a fluororesin material, for example, a PFA resin material.
  • a PFA resin material may be impregnated with a lubricating oil such as a refrigerator oil in advance.
  • the helical blade 25 By making the helical blade 25 itself self-lubricating, the helical blade 25 can smoothly enter and exit the spiral groove 28 of the mouthpiece 24, improving the sealing performance, while improving the helical blade. 25 Mechanical strength ⁇ Abrasion resistance can be improved.
  • the helical blade 25 is manufactured with high productivity on an injection molding machine and with high blade accuracy.
  • the inner diameter of the helical blade 25 is formed larger than the outer diameter of the roller 24 in consideration of assemblability and sealing performance, while having the same pitch as the spiral groove 28 of the roller 24.
  • Molded into The helical blade type compression mechanism 13 is assembled by fitting the helical blade 25 into the spiral groove 28 of the roller 24 with the diameter reduced forcibly, and the outer peripheral surface of the helical blade 25
  • the helical blade 25 is used to seal the inner peripheral surface of the cylinder with the helical blade 25 so as to be in elastic contact with the entire inner peripheral surface of the cylinder.
  • each compression chamber 30 is Due to the orbital motion (eccentric turning motion) of the roller 4, the roller 24 spirally moves in the axial direction, and the volume is gradually and continuously reduced while moving spirally.
  • the refrigerant gas sucked into the compression chamber 30 from the suction part 31 on the sub bearing 21 side of the helical blade type compression mechanism 13 3 receives a continuous compression action by the revolving motion of the roller 24, and becomes high pressure. It is discharged into the sealed case 11 through the discharge hole 32 on the main bearing 20 side. The refrigerant gas discharged into the sealed case 11 is discharged from the discharge port 33 to the outside through the inside of the sealed case 11.
  • a suction port 35 is formed on the same side of the sealed case 11 as the discharge port 33.
  • the suction port 35 communicates with a suction section 31 of the compressor mechanism 13 via a suction passage 36 in the closed case 11.
  • the suction passage 36 extends from the sub bearing 21 to the suction portion 31 of the compression mechanism 13 via the outer peripheral flange 23 b of the cylinder 23.
  • the roller 24 incorporated in the helical blade type compression mechanism 13 is configured as shown in FIGS. 3A and 3B. That is, the roller 24 has a spiral groove 28 on the outer peripheral surface, and a key groove 38 as an Oldham key which can be engaged with the Oldham mechanism 27 on one end surface.
  • the keyway 38 is formed radially on the roller end face as shown in Fig. 3B, and diametrically opposed. A pair is provided.
  • the keyway 38 includes a radially straight portion 38a extending radially outward and a relief R portion 38b, and is formed by machining such as end milling. Escape R part 38b is a semicircular arc-shaped part generated during processing.
  • the linear portion 38a of the key groove 38 engages with the engaging teeth 41 of the Oldham ring 40 constituting the Oldham mechanism 27 as Oldham keys, and guides the engaging teeth 41 slidably.
  • the R portion 38b is a relief portion that does not engage with the Oldham ring 40.
  • the Oldham ring 40 is configured as shown in FIGS. 4A and 4B.
  • the engaging teeth (engaging protrusion) 41 engageable with the key groove 38 of the roller 24, and on the other side engage the engaging groove 43 of the sub bearing 21.
  • Possible engagement teeth (engagement projections) 4 4 are integrally provided so as to be engageable.
  • the Oldham ring 40 is housed in the circumferential groove 45 of the sub bearing 21, and is prevented from rotating when the engaging tooth 44 engages with the engaging groove 43.
  • an outer peripheral flange 46 is formed on the outer peripheral surface of the mouthpiece 24 on which the key groove 38 is formed.
  • the outer peripheral flange 46 protrudes over the entire outer periphery from the remaining outer peripheral surface of the roller 24, and maintains the mechanical and physical strength of the end of the roller 24 on the key groove 38 forming side.
  • the outer peripheral flange 46 of the roller 24 is engaged with a peripheral groove 47 formed at the end of the cylinder 23, and regulates the axial movement of the mouthpiece 24 in the cylinder 23.
  • the roller 24 is formed such that the suction side end of the spiral groove 28 is at 0 degree, and when the spiral groove 28 is formed at a positive angle in the circumferential direction from 0 degree, the roller 24 has a negative side from almost 0 degree of the outer peripheral part.
  • a refrigerant gas suction port (suction portion) 48 is formed at the angular position of. Refrigerant gas suction port 48 is preferably provided at an appropriate angular position in the range of 0 to 190 degrees.
  • both ends of the spiral groove 28 of the roller 24 are recessed to form a relief portion 49 for a blade stopper.
  • the blade stopper escape portions 49 formed at both ends of the spiral groove 28 are formed at the same angular position in the rotation direction of the roller 24. The escape portion 48 restricts the movement of the helical blade 25.
  • one of the pair of key grooves 38 formed on the roller 24 is positioned at a required angle a within 90 degrees from the end of the spiral groove 28 as shown in FIG. 3B. Formed.
  • This portion is a position where the spiral groove 28 is interrupted, and the key groove 38 can be arranged. That is, when the suction side end, which is the start end of the spiral groove 28 of the roller 24, becomes 0 degree and the spiral groove 28 is formed at a plus side angle, the one key groove 38 extends in the radial direction.
  • the line is formed at the required angle ⁇ on the negative side, for example, within 90 degrees on the negative side.
  • the key groove 38 is preferably formed at an appropriate angular position from minus 30 degrees to minus 60 degrees.
  • the spiral groove 28 formed on the outer peripheral surface of the roller 24 and the key groove 38 formed on the roller end surface are arranged as shown in FIGS. 3 and 3 to form a spiral groove.
  • the groove 28 and the key groove 38 can be arranged efficiently, the wall thickness between the two grooves 28, 38 can be sufficiently ensured, and the interference between the two grooves 28, 38 can be prevented.
  • the efficient arrangement of the spiral groove 28 and the key groove 38 of the roller 24 reduces the overall length (axial length) of the roller 24, and the helical blade type compression mechanism 13 compactness can be achieved.
  • a lubricating oil 48 is stored in the lower part of the sealed case 11 as shown in FIG. 1, and the stored lubricating oil 50 is sucked up by the oil pump device 51 so that the crankshaft 18 It is supplied to the lubricating part.
  • the oil pump device 51 operates in conjunction with the rotation of the crankshaft 18 to perform a pumping operation.
  • the lubrication oil drainage is This is performed via the oil drainage mechanism 52.
  • the helical compressor 10 is driven by passing electricity through a power supply terminal 17 to the electric motor 12, and the mouth 16 of the electric motor 12 is rotated.
  • the rotational driving force of the rotor 21 is transmitted to the helicopter-type compression mechanism 13 via the crankshaft 18 and causes the roller 28 of the compression mechanism 19 to eccentrically rotate.
  • the roller 24 revolves with the rotation of the crankshaft 18.
  • the helical blade type compression mechanism 13 causes the helical blade 25 to move into and out of the spiral groove 28 of the roller 24 by the orbital motion (eccentric turning motion) of the roller 24. Due to the orbital motion of the roller 24, the compressed nitrogen 30 formed between the roller 24 and the cylinder 23 moves helically in the axial direction of the roller 24, and is compressed during this movement. The volume of the chamber 30 is gradually and continuously reduced, and the refrigerant gas undergoes a compression action.
  • the refrigerant gas introduced into the suction section 31 flows into the compression chamber 30, and spirals in the axial direction of the roller 24 as the roller 24 revolves. During this time, the pressure is increased due to the continuous compression action, and is discharged from the discharge hole 32 into the closed case 11.
  • the high-pressure refrigerant gas discharged into the closed case 11 is guided to the discharge port 33 through the inside of the closed case 11, and is discharged from the discharge port 33 to the refrigeration cycle.
  • the helical compressor 10 receives a continuous and smooth compression action by the helical blade type compressor mechanism 13, so that the generation of discharge pulsation can be prevented effectively and beforehand. Accordingly, high-pressure refrigerant gas that does not generate discharge pulsation is stably discharged from the discharge port 33 to the refrigeration cycle.
  • the rotation (rotation) of the roller 24 of the helical blade type compressor structure 13 is regulated by the Oldham mechanism 27, and the roller 24 revolves without rotating inside the cylinder 23.
  • the helical blade 25 is moved in and out of the spiral groove 28 of the roller 24 with the revolving motion of the mouthpiece 24.
  • the roller 24 constituting the helical blade type compression mechanism 13 utilizes the interrupted position on the end (start end) side of the spiral groove 28 formed on the outer peripheral surface, and does not interfere with the spiral groove 28 Since the key groove 38 of the Oldham key is formed as described above, the key groove 38 and the spiral groove 28 can be efficiently arranged. Even if the keyway 3S and the spiral groove 28 are formed in the roller 24, the overall length of the roller 24 can be shortened, so that a compact helical blade-type compression mechanism 13 can be provided.
  • FIG. 6A and 6B show a first modified example of the roller 24A incorporated in the helical blade type compression mechanism 13.
  • FIG. 6A and 6B show a first modified example of the roller 24A incorporated in the helical blade type compression mechanism 13.
  • the roller 24A is obtained by adding a concave relief portion 55 to the roller 24 shown in FIGS. 3A and 3B.
  • the escape portion 55 is formed by recessing the refrigerant gas inlet 48 side of the outer periphery of the roller 24A.
  • roller The other portions of 24A are not substantially different from the rollers 24 shown in FIGS. 3A and 3B, and thus the same reference numerals are given and the description is omitted.
  • the relief portion 55 is formed from the angle position of approximately 0 degree to the required angle on the negative side) 3, for example, minus 120 degrees.
  • the concave relief portion 55 formed on the outer peripheral surface of the roller 24 is formed such that the groove bottom becomes gradually shallower. Also in this case, it is possible to effectively and reliably prevent the escape portion 55, the spiral groove 28, and the lock groove 38 from interfering with each other, and have the same effect as that shown in the embodiment. It is not always necessary to form the concave escape portion 55 over an angular position of approximately 0 degrees to minus 120 degrees, and for example, may be in the range of 0 degrees to 60 degrees or 90 degrees.
  • 7A and 7B show a second modified example of the roller.
  • the roller 24B shown in this modification is an example in which a key groove 56 formed on the roller end face is extended inward in the radial direction.
  • the other parts of the roller 24B are not different from those shown in FIGS. 3A and 3B, and thus the same reference numerals are given and the description is omitted.
  • the length of the sliding portion of the key groove 56 formed on the roller end surface of the roller 24B can be increased, and even if the length of the sliding portion of the key groove 56 is increased, Interference between the groove 56 and the spiral groove 28 can be prevented.
  • the roller 24 C shown in this modified example has the outer shape of the roller 24 C of the key groove 57 forming portion protruding radially outward compared to the other roller outer diameter shapes,
  • the key groove 57 can be extended outward in the radial direction by the amount of the protrusion 58 formed.
  • the other roller portions are the same as the rollers 24 shown in FIGS. 3A and 3B except for the width of the outer peripheral flange 59, and therefore are denoted by the same reference numerals and description thereof is omitted.
  • the overall length of the roller 24 C is longer by the width of the outer peripheral flange 59 being wider than the roller 24 shown in FIGS. 3A and 3B.
  • a protruding portion 58 on the roller 24 C and protruding outward in the radial direction further than the outer peripheral flange 59 by using this protruding portion 58 to form a key groove 57,
  • the key groove 57 can be extended radially outward.
  • the acting force acting on the key groove 57 can be further reduced.
  • the sliding characteristics between the Oldham mechanism 27 and the keyway 57 formed on the end face of the roller 24 can be improved, and the reliability can be improved.
  • 9A and 9B show a fourth modification of the roller.
  • the key groove 5 7 is extended outward in the radial direction. Even if it is formed, it is possible to prevent the spiral groove 28 from contacting with the spiral groove 28, but it is not necessary to form the outer peripheral flange 46 wide. Therefore, by forming the outer peripheral surface of the roller 24D facing the formation position of the key groove 57 outward in the radial direction, and forming the key groove 57 by using the protrusion 58, the key groove is formed. 57 The length of the sliding part can be increased. The other rollers are not different from the rollers shown in FIGS. 3A and 3B, so the same reference numerals are given and the description is omitted. ⁇
  • FIGS. 9A and 9B even if the keyway 57 formed on the roller end face is extended outward in the radial direction, FIGS. Unlike the case shown in FIG. B, the overall length of the roller 24 D can be shortened.
  • the spiral formed on the outer peripheral surface of the mouth is The forming angle relationship between the groove 28 and the key groove formed on the roller end face is not substantially different from the roller shown in FIGS. 3A and 3B.
  • Each roller can have substantially the same operation and effect as the roller 24 shown in FIG.
  • the example in which the key groove is formed on the roller end face is shown.
  • the projections may be formed integrally with each other.
  • an engagement groove (key groove) for engaging with the protrusion is formed on the Oldham ring side.
  • an Oldham key is formed on the roller end face of the roller so as to engage with the Oldham ring in a concave and convex manner.
  • the Oldham key may be a key groove or an engagement projection.
  • the present invention is applied to a horizontal helical compressor
  • the present invention can be applied to a vertical helical compressor.
  • the positions where the suction port and the discharge port are formed are appropriately selected.
  • the spiral groove formed on the outer peripheral surface of the roller does not interfere with the key groove formed on the end surface of the roller.
  • this helical compressor efficiently arranges the spiral groove formed on the roller and the key groove of the Oldham key, so that the wall thickness between both grooves can be secured.
  • the compact helical blade-type compression mechanism can be achieved by making the rollers compact, and a compact and highly reliable helical compressor can be provided.

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

Abstract

L'invention porte sur un compresseur hélicoïdal (10) comportant à l'intérieur de son carter étanche (11) un moteur électrique (12) et un mécanisme (13) de compression entraîné par le moteur électrique (12). Ledit mécanisme (13) comprend un roulement principal (20), un roulement secondaire (21), un cylindre (23) un rouleau (24) placé excentriquement dans le cylindre (23), et une lame hélicoïdale (25) située entre le rouleau (24) et le cylindre (23). Le rouleau présente une rainure (28) en spirale formée à la surface de sa périphérie extérieure et une rainure radiale de languette (38) formée à la surface de l'extrémité du rouleau. Lorsque l'extrémité côté aspiration de la rainure en spirale est à zéro degré, la rainure en spirale fait du côté plus un angle supérieur à zéro, et la rainure de languette (38) se place à la position angulaire requise du côté moins. La rainure en spirale (28) et la rainure de languette (38) se trouvent alors placées respectivement sur la surface périphérique extérieure, et la surface de l'extrémité, du rouleau (24). Cette disposition donne un compresseur hélicoïdal dans lequel le rouleau comporte à la fois la rainure spirale et le joint Oldham, ce qui réduit l'encombrement et améliore la fiabilité.
PCT/JP2001/007613 2000-09-04 2001-09-03 Compresseur helicoidal Ceased WO2002020992A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2001282612A AU2001282612A1 (en) 2000-09-04 2001-09-03 Helical compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000-266544 2000-09-04
JP2000266544A JP2002070773A (ja) 2000-09-04 2000-09-04 ヘリカルコンプレッサ

Publications (1)

Publication Number Publication Date
WO2002020992A1 true WO2002020992A1 (fr) 2002-03-14

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PCT/JP2001/007613 Ceased WO2002020992A1 (fr) 2000-09-04 2001-09-03 Compresseur helicoidal

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JP (1) JP2002070773A (fr)
AU (1) AU2001282612A1 (fr)
WO (1) WO2002020992A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09242681A (ja) * 1996-03-05 1997-09-16 Toshiba Corp ヘリカルブレード式圧縮機
JPH11324955A (ja) * 1998-05-07 1999-11-26 Toshiba Corp ヘリカルブレード式圧縮機

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09242681A (ja) * 1996-03-05 1997-09-16 Toshiba Corp ヘリカルブレード式圧縮機
JPH11324955A (ja) * 1998-05-07 1999-11-26 Toshiba Corp ヘリカルブレード式圧縮機

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AU2001282612A1 (en) 2002-03-22
JP2002070773A (ja) 2002-03-08

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