WO2007052332A1 - Compresseur a vis a injection de liquide - Google Patents

Compresseur a vis a injection de liquide Download PDF

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Publication number
WO2007052332A1
WO2007052332A1 PCT/JP2005/020041 JP2005020041W WO2007052332A1 WO 2007052332 A1 WO2007052332 A1 WO 2007052332A1 JP 2005020041 W JP2005020041 W JP 2005020041W WO 2007052332 A1 WO2007052332 A1 WO 2007052332A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
suction
casing
line
bore
Prior art date
Application number
PCT/JP2005/020041
Other languages
English (en)
Japanese (ja)
Inventor
Yoshifusa Kubota
Yoshiyuki Kobayashi
Shigeru Muta
Yasuaki Endo
Original Assignee
Mayekawa Mfg. Co., Ltd
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 Mayekawa Mfg. Co., Ltd filed Critical Mayekawa Mfg. Co., Ltd
Priority to CA2626884A priority Critical patent/CA2626884C/fr
Priority to EP05805438.8A priority patent/EP1944513A4/fr
Priority to JP2007542181A priority patent/JP4702639B2/ja
Priority to PCT/JP2005/020041 priority patent/WO2007052332A1/fr
Publication of WO2007052332A1 publication Critical patent/WO2007052332A1/fr
Priority to US12/111,624 priority patent/US20080253914A1/en

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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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2240/00—Components
    • F04C2240/10—Stators

Definitions

  • the present invention sucks and closes a lip portion on the bore surface in order to prevent backflow of liquid such as oil and water injected into the bore surface of a casing housing a pair of male and female screw rotors to the suction port side.
  • the present invention relates to a liquid injection screw compressor provided in a region up to a portion separated by one tooth groove on the downstream side from the suction confinement line.
  • a pair of male and female screw rotors are squeezed inside a casing to form a working chamber, and a liquid such as oil or water is injected into the working chamber to compress in a gas-liquid mixed phase state.
  • a compressor is used.
  • the liquid injection type is widely used because it has high efficiency even at low speeds due to the cooling action, sealing action or lubrication action of the injection liquid.
  • the gap between the tooth tip of the rotor and the bore surface is safe in areas where airtightness between adjacent tooth spaces is important, such as in the compression process. It can be held as small as possible within the limits that guarantee smooth and smooth operation.
  • this bore surface is referred to as a “main bore surface”.
  • the bore surface in this portion is enlarged in the radial direction compared to the main bore surface, and this bore surface is referred to as an “expanded bore surface”.
  • Patent Document 1 Japanese Patent Publication No. 42-10027
  • Patent Document 2 Japanese Patent Laid-Open No. 3-194183
  • Patent Document 3 Japanese Patent Laid-Open No. 11-13661
  • a liquid provided with a powerful lip portion is disclosed.
  • An injection screw compressor is disclosed.
  • Patent Document 1 as shown in FIG. 1 and FIG. 2 of Patent Document 1, a lip portion 44 is provided at the inlet portion of the casing 10 between the gas suction port 24 and the enlarged bore portion 40. Therefore, it is disclosed that heat flowing back from the compression chamber formed between the rotors and heat exchange between the fluid and the gas flowing in from the suction port 24 are reduced.
  • a lip-shaped edge 39 called a lip is provided on the suction side end surface of the casing 3 in FIG. 1, and the oil in the enlarged bores 7 and 8 flows out to the suction port side by the lip 39. It is disclosed that the suction gas is warmed to prevent a reduction in the filling efficiency of the rotor.
  • Patent Document 3 the reverse flow of oil injected into the working chamber floats as an oil mist in the suction chamber, and heats the suction air in the middle of suction, causing so-called “intake air heating", which is the compressed gas
  • intake air heating which is the compressed gas
  • Patent Document 3 a lip portion 5 protruding toward the screw rotor side is provided on the end surface on the suction port side of the casing 3 that accommodates the screw rotor, and a gap between the screw mouth and the lip portion 5 is further provided.
  • Inlet air heating prevention wall 9 is installed to prevent oil mist from leaking to the inlet side.
  • FIG. 9 shows a casing of a conventional screw rotor provided with a powerful lip portion, where (a) shows the upper side of the casing and (b) shows the lower side of the casing divided for convenience. .
  • a space for accommodating the male and female screw rotors is formed inside the casing 01, and the male rotor side main bore surface is in contact with the teeth of the male and female rotors with a slight gap.
  • a lip portion 04 projecting inward along the suction port side end surface of the casing 01 is provided, and a suction confinement line 05 is formed at the boundary between the main bore surfaces 02a, 02b and the enlarged bore surfaces 03a, 03b. .
  • the screw-shaped tooth groove carved in the rotor is independent between a male and female pair.
  • Form a working space While this working space communicates with the enlarged bore surfaces 03a and 03b, this working space gradually expands and sucks the suction loca gas, and passes through the confinement line 05 when the maximum volume is reached. It becomes a sealed space sealed with 03a and 03b. After the working space becomes a sealed space in this way, the working space is gradually narrowed and the gas in the working space is compressed, and then the discharge loci are discharged.
  • liquids such as oil and water are injected into the working space during the compression process in order to provide cooling, sealing, and lubrication.
  • FIG. 10 schematically shows a bore surface of a conventional screw rotor casing.
  • FIG. 10 (a) is a view of the suction confinement line and the lip portion attached to the casing as seen through the upper force
  • FIG. 10 (b) is a developed view thereof.
  • the suction confinement line 05 is formed at the boundary between the main bore surfaces 02a and 02b and the enlarged bore surfaces 03a and 03b, and the suction side end surface of the casing There is a lip 04 protruding from the base.
  • the working space formed between the male screw rotor and the female screw rotor faces the enlarged bore surfaces 03a and 03b of the rotor casing on the suction port side, and the working space gradually expands. Inhalation loca Inhales gas. After the working space reaches the maximum volume, the working space moves to the main bore surfaces 02a and 02b side by passing through the suction confinement line 05 and becomes a sealed space. Thereafter, the working gas moving space is reduced, and the gas in the working space is compressed. The compressed gas is discharged from the discharge side end face 07 of the rotor casing to the discharge port.
  • liquids such as oil and water applied to the working space during the compression process by the lip portion 04 leak to the low pressure suction side, accumulate on the enlarged bore surfaces 03a and 03b, and scatter from there to the suction end surface 06 side. Is blocked by the lip 04.
  • Patent Document 1 Japanese Patent Publication No. 42-10027
  • Patent Document 2 JP-A-3-194183
  • Patent Document 3 Japanese Patent Laid-Open No. 11-13661
  • the suction port since the lip portion is provided on the suction side end surface of the rotor casing, the suction port must be installed outside the lip portion, The inlet opening area of the suction side end face of the rotor casing is narrow, so when recording the suction inlet connected to the suction end face of the rotor casing integrally with the rotor casing, the inside of the rotor casing bore It is difficult to insert a child.
  • suction area to the rotor tooth is only possible by securing a space in the axial direction, which causes suction resistance of suction gas when operating at high speed.
  • the present invention provides oil, water, etc. from a high-pressure working space during a compression stroke of the working space formed by a screw rotor in a liquid jet screw compressor.
  • the suction resistance of the gas sucked from the inlet to the rotor casing is reduced to improve volumetric efficiency, and the molding of the casing is simplified.
  • the objective is to realize a liquid injection screw compressor that can reduce manufacturing costs.
  • the present invention provides a compact structure that does not extend the drive mechanism of the internal volume ratio variable valve to the suction side long in a variable internal volume ratio type screw compressor equipped with an internal volume ratio variable valve that makes the compression ratio variable.
  • the purpose is to further reduce manufacturing costs.
  • a liquid jet screw compressor of the present invention includes: A pair of male and female screw rotors;
  • a rotor casing having a bore for accommodating the pair of screw rotors; a gas inlet and a gas outlet provided at both ends of the rotor casing and communicating with the bore;
  • a liquid-injection-type screw compressor comprising a lip portion projecting from a bore surface upstream of the suction confinement line of the rotor casing in order to prevent backflow of liquid from the bore surface to the suction port side
  • the lip portion is arranged in a region surrounded by the suction confinement line and the suction confinement line force on the enlarged bore surface side by a line separated by one tooth groove of the screw rotor.
  • the lip portion for preventing the back flow of the liquid to the suction port side is separated from the suction confinement line and the one tooth groove of the screw rotor downstream from the suction confinement line.
  • the lip is provided in a region closer to the suction confinement line than in the conventional method, so that liquid leaks from the compressed working space to the low pressure inlet side.
  • the suction confinement line in the vicinity of the bore intersection where the male rotor casing and the female rotor casing intersect with each other is a straight line arranged in a direction perpendicular to the bore intersection line.
  • the front edge (the side near the suction binding line) of the lip portion that is spaced and opposed in the rotor axial direction has a curved shape protruding toward the suction closing line side, and the rear edge of the lip portion is the suction confinement
  • the lip portion may be formed thick by forming a linear shape parallel to the linear portion of the line. As a result, it is possible to reliably prevent liquid leakage at the bore intersection.
  • Suction confinement formed in male rotor casing with said straight portion of suction confinement line A straight line is formed in the direction perpendicular to the bore intersection line from the intersection with the bore intersection line toward the female rotor casing, and the linear portion is formed in the female rotor casing. Extend to the position where it crosses the suction confinement line,
  • the front edge of the lip portion formed on the male rotor casing and the bore intersecting line Starting from the intersection of the front edge of the lip portion formed on the male rotor casing and the bore intersecting line, the front edge of the lip portion that is spaced apart and opposed to the linear portion in the rotor axial direction
  • a female-side rotor casing having a curved shape projecting toward the intake confinement line and a rear edge of the lip portion formed on the male-side rotor casing and an intersection of the bore intersection line with the bore crossing line.
  • the lip portion is made thick by forming a straight line arranged perpendicular to the bore crossing line toward
  • the front edge and the rear edge of the lip portion are extended to a position where they intersect with the front edge and the rear edge of the lip portion formed in the female rotor casing.
  • the rotor casing is configured such that the gas suction port is formed integrally or divided on the upstream side of the lip portion installation position.
  • the lip portion is disposed close to the suction confinement line side, the bore surface on the suction port side of the rotor casing can be reduced. Therefore, the gas suction port is formed integrally with the rotor casing. This is possible.
  • the rotor casing can be reduced in size and space, and the restriction on the installation position of the suction port with respect to the rotor casing is greatly relaxed, and the design freedom of the suction port is greatly increased.
  • the end face of the lip portion facing the screw rotor has a labyrinth effect.
  • the liquid leakage prevention effect can be further improved by providing roughness (for example, rusted skin) or unevenness on the end face of the lip portion facing the screw rotor.
  • the pair of screw rotors are different diameter rotors having different diameters
  • the diameter of the male screw rotor is made larger than the diameter of the female screw rotor
  • the number of teeth of the male screw rotor is set to the male female screw. Compared to rotors with the same rotor diameter Do more.
  • the distance between tooth tips (tooth gap width) of the male screw rotor can be shortened, and the lip portion can be provided at a position closer to the suction confinement line, thereby further improving the effect of preventing liquid leakage. And simplification of the casing shape can be achieved.
  • the lip portion is provided on the bore surface of the lower casing, it is possible to easily prevent the liquid accumulated on the lower bore surface due to gravity from being scattered to the suction port side.
  • a simplified configuration can be realized.
  • a capacity control valve and an internal volume ratio variable valve are provided below the male and female screw rotors in the rotor casing.
  • the displacement control valve has a notch for restricting a gas discharge opening between the rotor casing end surface and a valve drive shaft extending to the suction casing side on the rotor suction side at a discharge side end portion thereof.
  • the valve drive shaft is protruded to the suction side casing wall side through the internal volume ratio variable valve storage space provided on the suction side facing the rotor, and is connected to a drive source provided on the suction side casing wall side.
  • the displacement control valve is configured to be movable forward and backward toward the rotor discharge side via the drive source and the valve drive shaft,
  • the internal volume ratio variable valve stored in the storage space is disposed adjacent to the suction side end surface of the capacity control valve, and has positioning means for varying the position in the rotor discharge direction.
  • the volume ratio variable valve is adjusted by positioning to a predetermined position by the positioning means,
  • the internal capacity may be configured such that the capacity control valve is slidably controlled via the drive source and the valve drive shaft so that the gap force with the internal volume ratio variable valve is also adjusted by the amount of gas that bypasses to the suction side.
  • the compressor itself can be downsized and a compressor having three compression ratios of low, medium, and high compression ratios can be obtained only on the suction side casing side.
  • the conventional internal volume ratio variable valve has a fixed shaft extending to the discharge side, and a discharge side casing.
  • the positioning means of the internal volume ratio variable valve is preferably arranged concentrically on the outer periphery of the valve drive shaft of the capacity control valve.
  • a hollow shaft having a threaded portion that engages with the hollow shaft, and a rotating rod disposed in a direction intersecting the hollow shaft via a connecting portion capable of transmitting rotational motion to the hollow shaft. If the internal volume ratio variable valve is configured to be positioned at a predetermined position by rotating the valve, the drive mechanism of the internal volume ratio variable valve that does not need to extend the fixed shaft on the discharge side can be compactly integrated. it can.
  • the connecting portion may be constituted by, for example, a bevel gear or a screw gear.
  • the lip portion for preventing the back flow of the liquid from the bore surface of the rotor casing to the suction port side is provided with the suction confinement line and the suction confinement linear force to the screw side toward the enlarged bore surface. Dispersion of liquid leaking from the working space formed by the male and female screw rotors during the compression process to the inlet side due to the arrangement within the area surrounded by the line separated by the tooth gap. Can be effectively prevented.
  • the lip portion can be arranged close to the suction confinement line, there is no need for rotor casing from the lip portion to the suction port side, and the shape of the rotor casing can be simplified.
  • the suction resistance of the compressor can be reduced, which improves the volumetric efficiency of the compressor.
  • the lip portion in a region close to the suction confinement line, the bore surface closer to the suction port than the lip portion can be reduced, and the suction port can be integrally formed with the rotor casing.
  • the suction confinement line in the vicinity of the bore intersection where the male-side rotor casing and the female-side rotor casing intersect with each other is a straight line arranged in a direction perpendicular to the bore intersection line.
  • the front edge of the lip portion that is disposed opposite to the linear portion in the rotor axial direction has a curved shape protruding toward the suction confinement line side, and the rear edge of the lip portion is By making the lip portion thick by forming a straight line parallel to the straight part of the suction confinement line, and more preferably, the straight part of the suction confinement line is connected to the male rotor
  • the suction confinement line formed in the singe is arranged in a direction perpendicular to the bore crossing line from the intersection with the bore crossing line toward the female side rotor singing, and the linear part is placed in the female side rotaque.
  • the leading edge of the lip portion that extends to a position that intersects the suction confinement line formed in a single piece and is opposed to the linear portion in the rotor axial direction is used as a male rotor casing.
  • a curved shape projecting toward the suction confinement line starting from the intersection of the formed front edge of the lip portion and the bore crossing line, and the rear edge of the lip portion is formed on the male rotor casing.
  • the lip portion is made thick, and the lip portion is made thick.
  • the pair of screw rotors are different-diameter rotors having different diameters
  • the diameter of the male screw rotor is larger than the diameter of the female screw rotor
  • the number of teeth of the male screw rotor is equal to the diameter of the male and female screw rotors.
  • a capacity control valve and an internal volume ratio variable valve are provided below the male and female screw rotors in the rotor casing, and the capacity control valve has the rotor casing end face at the discharge side end thereof.
  • a valve drive shaft extending to the suction casing side on the rotor suction side, the internal volume provided on the suction side facing the rotor
  • the capacity control valve is connected to a drive source provided on the suction side casing wall side by projecting to the suction side casing wall side through the ratio variable valve storage space, and the capacity control valve is connected via the drive source and the valve drive shaft.
  • the internal volume ratio variable valve accommodated in the storage space is configured to freely move forward and backward toward the rotor discharge side, and the suction side end surface of the capacity control valve
  • the internal volume ratio is adjusted by positioning the internal volume ratio variable valve at a predetermined position by the positioning means, and the internal volume ratio is adjusted.
  • the capacity is configured such that the capacity control valve is slidably controlled via the drive source and the valve drive shaft so as to be adjusted by an amount of gas that is biased from the gap with the internal volume ratio variable valve to the suction side.
  • the suction side casing part can be shared by replacing only the rotor casing part.
  • the suction side casing part and the discharge side casing part can be made common and the low compression ratio can be reduced.
  • a compressor having the following compression ratio, a compressor having a medium compression ratio, a compressor having a high compression ratio, and three types of compressors can be obtained.
  • the positioning means of the internal volume ratio variable valve is arranged concentrically on the outer periphery of the valve drive shaft of the capacity control valve, and the screw portion to which the internal volume ratio variable valve is screwed is arranged on the outer periphery. And a rotary rod disposed in a direction intersecting the hollow shaft via a connecting portion capable of transmitting rotational motion to the hollow shaft, and the internal volume is determined by rotating the rotary rod. If the ratio variable valve is configured to be positioned at a predetermined position, the drive mechanism of the internal volume ratio variable valve that does not require a fixed shaft to extend long on the discharge side can be compactly assembled.
  • FIG. 1 (a) is an explanatory view of the rotor casing according to the first embodiment of the present invention as seen through the upper force;
  • FIG. 2 (a) is a perspective view showing the upper side of the rotor casing of the first embodiment, and (b) is a perspective view showing the lower side of the rotor casing in three dimensions.
  • FIG. 3 is a partial perspective view of the rotor casing of the first embodiment.
  • FIG. 4 is a longitudinal plan view of a second embodiment of the present invention.
  • FIG. 5 is a vertical elevational view of the second embodiment.
  • FIG. 6 is a development view showing a different diameter rotor and a suction confinement line of the second embodiment.
  • FIG. 7 is an explanatory view showing a different diameter rotor of the second embodiment.
  • FIG. 8 is a perspective view showing a modification of the second embodiment.
  • FIG. 9 (a) is a perspective view showing a conventional compressor rotor upper side and (b) a three-dimensional perspective view of the lower rotor casing.
  • FIG. 10 (a) is an explanatory view of a conventional rotor casing seen through from above, and (b) is an expanded view thereof.
  • variable valve internal volume ratio variable valve
  • FIG. 1 (a) is an explanatory view of the rotor casing according to the first embodiment of the present invention seen through the upper force
  • FIG. 1 (b) is a development view thereof
  • FIG. 2 (a) is the first embodiment.
  • (B) is a perspective view showing a three-dimensional view of the lower side of the rotor casing
  • FIG. 3 is a partial perspective view of the rotor casing of the first embodiment
  • FIG. FIG. 5 is a longitudinal plan view of the second embodiment of the invention.
  • Fig. 6 is a vertical elevational view of the second embodiment
  • Fig. 6 is a development view showing the different diameter rotor and suction confinement line of the second embodiment
  • Fig. 7 is an explanation showing the different diameter rotor of the second embodiment.
  • FIG. 8 is a perspective view showing a modification of the second embodiment.
  • FIG. 1 schematically shows the bore surface of the rotor casing of the screw compressor of the present invention.
  • FIG. 1 (a) is a perspective view of the suction confinement line and the lip portion attached to the casing.
  • (B) is a developed view thereof.
  • the rotor casing is divided into upper and lower parts for convenience, and the bore surface of the rotor casing is shown.
  • D is the outer diameter of the rotor tip (mm)
  • c is the clearance of each part.
  • the suction confinement line 5 includes a bore intersection line 8 where a bore surface of the male rotor side casing la intersects a bore surface of the female rotor side casing lb, and a male rotor side casing la side suction confinement line 5a. From the intersection point a toward the female rotor side casing lb, it has a straight portion 5c that extends at right angles to the bore intersection line 8 and extends to one point that intersects the closed line 5b of the female rotor side casing lb.
  • the front edge 4d of the lip portion 4c that is disposed opposite to the straight line portion 5c in the rotor axial direction is located at a position separated from the straight line portion 5c by one tooth gap in the lip portion corresponding to the straight line portion 5c.
  • the front edge of the lip formed on the male rotor casing and the intersection line b of the bore line 8 are curved starting from the suction confinement line 5 and the rear edge 4e of the lip part 4c is male. From the intersection c of the rear edge of the lip formed in the side rotor casing and the bore intersection line 8 to the starting point, the straight line is arranged perpendicularly to the bore intersection line 8 toward the female side rotor casing.
  • the lip portion 4c is formed thick, and the front edge 4d and the rear edge 4e of the lip portion 4c are extended to a position where the front edge and the rear edge of the lip portion formed on the female rotor casing intersect.
  • Lips 4 prevent liquids such as oil and water added to the working space during the compression process from leaking to the low-pressure suction side, collecting on the enlarged bore surfaces 3a, 3b, and splashing from there to the suction port side. ing.
  • the lip portion 4 is provided at an interval of one tooth gap from the suction confinement line 5, and the suction confinement line 5 is compared with the conventional configuration. Since the liquid is supplied to the working space formed between the male and female rotors during the compression process, it is more effectively prevented from leaking to the low-pressure inlet side than the conventional method. As well as being able to eliminate the casing part on the suction port 9 side from the lip part 4, it is possible to reduce the suction resistance when sucking gas into the working space of the suction port 9 and to reduce the volume efficiency of the compressor. Can be improved.
  • a straight line portion 5c of the suction confinement line 5 is provided at a right angle to the bore intersection line 8, and one straight groove is separated from the straight line portion 5c, so that the suction confinement line is provided.
  • a thick-walled lip portion 4c consisting of a leading edge 4d ejected in a curved shape on the side 5 and a trailing edge 4e arranged perpendicular to the bore intersection line 8
  • male and female in the vicinity of the bore intersection line 8 are provided. Liquid leakage from the working space of the rotor casing to the inlet side can be reliably prevented.
  • the casing portion on the suction port 9 side from the lip portion 4 can be eliminated, the structure of the rotor casing can be simplified, and the position of the suction port can be brought closer to the rotor casing side, so that the rotor casing can be made closer. And the suction port can be manufactured in one piece, the manufacturing process can be simplified, and the manufacturing cost can be reduced.
  • the second embodiment uses a different diameter rotor having a male rotor diameter larger than the female rotor diameter.
  • the male rotor has five teeth and the female rotor has six teeth. It has.
  • reference numeral 11 denotes a casing for accommodating both male and female screw rotors.
  • a casing 13 for forming a suction port 12 is formed in the casing 11.
  • a male rotor 22 and a female rotor 23 shown in FIG. 7 are housed inside the rotor casing 11, but illustration thereof is omitted.
  • 14 is a male rotor shaft, thrust bearing 16 and radius Supported by bearings 17 and 18.
  • a female rotor shaft 15 is supported by a thrust bearing 19 and radial bearings 20, 21.
  • the shaft end portion 14a of the male rotor shaft 14 has a mechanical seal 24 as a shaft seal device, and the shaft end portion 14a is connected to an output shaft of an electric motor (not shown) as a rotational drive source.
  • the casing 26 forming the discharge port 25 is manufactured separately from the rotor casing 11 and is connected to the rotor casing 11 by connection bolts 27.
  • the lower part of the rotor casing 11 is equipped with a slide valve 28 that controls the capacity (intake gas flow rate) of the compressor by sliding in the rotor axial direction.
  • the slide valve 28 is slid in the rotor axial direction by a push rod 29. The amount is adjusted.
  • the push rod 29 is driven by supplying hydraulic oil to the hydraulic cylinder 30 to the left and right hydraulic chambers 30a and 3 Ob.
  • a manual Vi variable mechanism 31 capable of optimizing the internal volume ratio (Vi) according to operating conditions is provided at the center of the push rod 29.
  • the casing 35 containing the Vi variable mechanism 31 is connected to the casing 13 by a connection bolt 36, and the hydraulic cylinder 30 is connected to the casing 35.
  • 37 is a Vi variable valve, which is screwed into a screw portion 38a provided on the outer periphery of a hollow shaft 38 that is concentrically mounted on the outer periphery of a push rod 29 having a circular cross section. Is moved in the rotor axial direction by the rotation of the hollow shaft 38.
  • 39a is a bevel gear provided at the suction side end of the hollow shaft 38, and meshes with a bevel gear 39b provided at the end of the rotary rod 40 provided in a direction orthogonal to the hollow shaft 38.
  • FIG. 6 shows a male screw rotor 22 and a female screw rotor 23 used in the second embodiment, and a suction confinement line 32 formed on the inner surface of the rotor casing.
  • the male rotor 22 This is a different diameter rotor having a larger diameter.
  • the male rotor 22 has five tooth tips in the circumferential direction
  • the female rotor 23 has six tooth grooves in the circumferential direction.
  • FIG. 4 shows the suction confinement line 32 and the lip portion 33 for convenience.
  • the lip 33 is formed at a position separated from the suction confinement line 32 by one tooth gap toward the suction port.
  • the suction confinement line 32 has a portion 32a formed on the male rotor side casing where the male rotor side casing 1 la and the female rotor side casing 1 lb intersect.
  • a straight portion 32c extends from the point a intersecting with the bore intersecting line 34 in a direction perpendicular to the bore intersecting line 34 toward the female rotor side, and extends to a position intersecting with the portion 32b formed on the female rotor side casing rib.
  • the straight portion 5c of the suction binding line 32 is separated from the tooth groove, and the suction lip is closed from the intersection b of the front edge of the lip portion 33a formed on the male rotor casing 11a and the bore intersection line 34.
  • the front edge 33d discharged in a curved manner toward the line 32 and the rear edge of the lip 33a formed on the male rotor casing 11a and the intersection line 34 of the bore intersection line 34 are arranged at right angles to the bore intersection line 34.
  • a thick lip portion 33c formed from the rear edge 33e is provided.
  • the lip portion 33 is formed at a position separated from the suction confinement line 32 by one tooth gap toward the suction port side, as in the first embodiment shown in FIG. Therefore, it is possible to reliably prevent liquid from leaking from the working space to the suction port side during the compression process and to be configured as described above near the bore intersection line. Leakage can be reliably prevented.
  • the rotor casing 11 on the inlet side can be removed from the lip 33 installation position, As a result, a large space can be provided between the bore surface of the rotor casing and the suction port 12, so that the suction resistance of the gas from the suction port 12 can be reduced, thereby improving the volumetric efficiency of the compressor. be able to.
  • the position of the suction port 12 can be moved to the side of the mouth packaging 11 and thereby the casing 13 forming the suction port 12 is formed.
  • the rotor casing 11 can be integrally manufactured, which makes it possible to reduce the size and space of the compressor casing and greatly reduce the manufacturing cost of the compressor.
  • the distance L between the axis i of the inlet 12 and the axis o of the outlet 25 can always be designed to be constant in the same model, which allows mechanization of the compressor casing production line and robotics. It becomes possible.
  • the compressor itself can be downsized, and a compressor having three compression ratios of low, medium, and high compression ratio can be obtained only on the suction side casing side.
  • the conventional Vi variable valve has an increased force due to the fixed shaft extending on the discharge side and being fixed outside the casing on the discharge side.
  • the Vi variable valve 37 positioning means In a direction orthogonal to the hollow shaft 38 via the hollow shaft 38 concentrically arranged on the outer periphery of the push rod 29 that is the drive shaft of the slide valve 28, the hollow shaft 38, and the bevel gears 39a and 39b.
  • the connecting portion between the rotary shaft 40 and the hollow shaft 38 may be replaced with a screw gear as shown in FIG. 8 instead of the bevel gears 39a and 39b of the second embodiment.
  • the bevel gear has the advantage that there is some backlash between the gears.
  • the screw gear has the advantage that there is no backlash between the gears.
  • a liquid such as oil or water having a compression chamber force formed by a screw rotor Leakage due to backflow to the suction side can be prevented more effectively than the conventional method, and the volume resistance is improved by reducing the suction resistance of the gas sucked from the suction port.
  • a liquid injection type screw compressor capable of reducing the manufacturing cost can be realized.

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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 à injection de liquide dans lequel, dans une course de compression d’un espace de fonctionnement formé par des rotors mâle et femelle, des liquides tels que de l’huile ou de l’eau sont empêchés de fuir à partir de l’espace de fonctionnement haute pression jusqu’au côté d’ouverture d’aspiration, la résistance à l’aspiration de gaz aspiré à partir de l’ouverture d’aspiration vers un carter de rotor est réduite pour optimiser le rendement volumétrique, et le façonnage de la forme du carter est simplifié. Le compresseur à vis à injection de liquide possède la paire mâle et femelle de rotors à vis, le carter rotateur (1a, 1b) qui possède un alésage pour recevoir les rotors, une ouverture d’aspiration de gaz et une ouverture d’évacuation de gaz qui sont prévues dans les deux sections d’extrémité du carter et communiquent avec l’alésage, et une section de lèvre (4) en saillie à partir d’une surface d’alésage (2) positionnée davantage sur le côté amont qu’une conduite de fermeture d’aspiration (5) du carter afin d’empêcher un refoulement du liquide à partir de la surface d’alésage jusqu’au côté d’ouverture d’aspiration. La section de lèvre (4) est positionnée dans une région entourée par la conduite de fermeture d’aspiration (5) et une conduite séparée par une distance d’une rainure de dent des rotors à partir de la conduite de fermeture d’aspiration (5) jusqu’au côté d’ouverture d’aspiration.
PCT/JP2005/020041 2005-10-31 2005-10-31 Compresseur a vis a injection de liquide WO2007052332A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CA2626884A CA2626884C (fr) 2005-10-31 2005-10-31 Compresseur a vis a injection de liquide
EP05805438.8A EP1944513A4 (fr) 2005-10-31 2005-10-31 Compresseur a vis a injection de liquide
JP2007542181A JP4702639B2 (ja) 2005-10-31 2005-10-31 液噴射式スクリュー圧縮機
PCT/JP2005/020041 WO2007052332A1 (fr) 2005-10-31 2005-10-31 Compresseur a vis a injection de liquide
US12/111,624 US20080253914A1 (en) 2005-10-31 2008-04-29 Liquid injection type screw compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2005/020041 WO2007052332A1 (fr) 2005-10-31 2005-10-31 Compresseur a vis a injection de liquide

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US12/111,624 Continuation US20080253914A1 (en) 2005-10-31 2008-04-29 Liquid injection type screw compressor

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WO2007052332A1 true WO2007052332A1 (fr) 2007-05-10

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US (1) US20080253914A1 (fr)
EP (1) EP1944513A4 (fr)
JP (1) JP4702639B2 (fr)
CA (1) CA2626884C (fr)
WO (1) WO2007052332A1 (fr)

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Publication number Priority date Publication date Assignee Title
JP5798331B2 (ja) * 2011-02-08 2015-10-21 株式会社神戸製鋼所 水噴射式スクリュ圧縮機
US10844860B2 (en) 2018-12-21 2020-11-24 Trane International Inc. Method of improved control for variable volume ratio valve
JP7124954B2 (ja) * 2019-03-08 2022-08-24 株式会社島津製作所 はすば歯車ポンプまたはモータ

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JPS5675994A (en) * 1979-11-21 1981-06-23 Hitachi Ltd Multieffect screw compressor
JPS5844289A (ja) * 1981-09-09 1983-03-15 Hitachi Ltd スクリユ圧縮機
JPS5949392A (ja) * 1982-09-11 1984-03-21 Mayekawa Mfg Co Ltd スクリユ−式圧縮機の吐出ポ−トの開度変更及び容量制御装置
JPS62180688U (fr) * 1986-05-09 1987-11-16
JPH03194183A (ja) * 1989-12-22 1991-08-23 Hitachi Ltd 液噴射式スクリュ流体機械
JPH07279678A (ja) * 1994-04-15 1995-10-27 Tochigi Fuji Ind Co Ltd スクリュー式過給機
JPH1113661A (ja) * 1997-06-25 1999-01-19 Hitachi Ltd スクリュー圧縮機
JP2004137934A (ja) * 2002-10-16 2004-05-13 Daikin Ind Ltd 可変ｖｉ式インバータスクリュー圧縮機

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BE653766A (fr) * 1963-10-01 1965-01-18
NO117317B (fr) * 1964-03-20 1969-07-28 Svenska Rotor Maskiner Ab
GB1361604A (en) * 1970-07-09 1974-07-30 Svenska Rotor Maskiner Ab Meshing screw rotor positive-displacement machines
DE3120943A1 (de) * 1981-05-26 1982-12-16 Isartaler Schraubenkompressoren GmbH, 8192 Geretsried "schraubenverdichter"
SE428043C (sv) * 1981-09-15 1989-12-14 Stal Refrigeration Ab Kompressor med radiellt inlopp till en skruvformig rotor
FR2530742B1 (fr) * 1982-07-22 1987-06-26 Dba Compresseur volumetrique a vis

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5675994A (en) * 1979-11-21 1981-06-23 Hitachi Ltd Multieffect screw compressor
JPS5844289A (ja) * 1981-09-09 1983-03-15 Hitachi Ltd スクリユ圧縮機
JPS5949392A (ja) * 1982-09-11 1984-03-21 Mayekawa Mfg Co Ltd スクリユ−式圧縮機の吐出ポ−トの開度変更及び容量制御装置
JPS62180688U (fr) * 1986-05-09 1987-11-16
JPH03194183A (ja) * 1989-12-22 1991-08-23 Hitachi Ltd 液噴射式スクリュ流体機械
JPH07279678A (ja) * 1994-04-15 1995-10-27 Tochigi Fuji Ind Co Ltd スクリュー式過給機
JPH1113661A (ja) * 1997-06-25 1999-01-19 Hitachi Ltd スクリュー圧縮機
JP2004137934A (ja) * 2002-10-16 2004-05-13 Daikin Ind Ltd 可変ｖｉ式インバータスクリュー圧縮機

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Title
See also references of EP1944513A4 *

Also Published As

Publication number Publication date
JPWO2007052332A1 (ja) 2009-04-30
CA2626884C (fr) 2012-01-24
CA2626884A1 (fr) 2007-05-10
EP1944513A1 (fr) 2008-07-16
US20080253914A1 (en) 2008-10-16
JP4702639B2 (ja) 2011-06-15
EP1944513A4 (fr) 2013-05-29

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