US20120058001A1 - Screw compressor with economizer - Google Patents
Screw compressor with economizer Download PDFInfo
- Publication number
- US20120058001A1 US20120058001A1 US13/148,943 US201013148943A US2012058001A1 US 20120058001 A1 US20120058001 A1 US 20120058001A1 US 201013148943 A US201013148943 A US 201013148943A US 2012058001 A1 US2012058001 A1 US 2012058001A1
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- United States
- Prior art keywords
- gas
- screw compressor
- supply hole
- male rotor
- 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.)
- Abandoned
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- 230000003872 anastomosis Effects 0.000 claims description 6
- 238000000034 method Methods 0.000 description 8
- 238000010586 diagram Methods 0.000 description 5
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Classifications
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- 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
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- 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
- F04C2250/00—Geometry
- F04C2250/10—Geometry of the inlet or outlet
- F04C2250/101—Geometry of the inlet or outlet of the inlet
Definitions
- the present invention relates to a screw compressor, more particularly to a screw compressor with economizer.
- FIGS. 1A-2B refrigerating cycle Systems 100 ′, 100 ′′ are illustrated.
- FIG. 1A is a schematic view of the refrigerating cycle system 100 ′ with a heat-exchange type economizer 3 ′.
- the refrigerating cycle system 100 ′ consists of a compressor 6 ′ connecting with a condenser 1 ′, an evaporator 5 ′ and the heat-exchange type economizer 3 ′.
- FIG. 1B is a Pressure-Enthalpy diagram of the refrigerating cycle system 100 ′ with the heat-exchange type economizer 3 ′.
- FIG. 2A is a schematic view of the refrigerating cycle system 100 ′′ with a flash-type economizer 3 ′′ and FIG. 2B is a Pressure-Enthalpy diagram of the refrigerating cycle system 100 ′′ with the flash-type economizer 3 ′′.
- the refrigerating cycle system 100 ′′ consists of a compressor 6 ′′ connecting with a condenser 1 ′′, an evaporator 5 ′′ and the heat-exchange type economizer 3 ′′.
- a gas-supply hole 10 ′ of an economizer of the conventional screw compressor is arranged along a radial direction to communicate with a tooth channel 60 ′ from time to time for gas supply.
- the tooth channel 60 ′ is defined by two adjacent teeth 301 ′, 302 ′ of a male rotor 30 ′.
- FIG. 4 illustrates a gas-supply process of the conventional radially-arranged gas-supply hole 10 ′ of the economizer.
- the rotating angle of the rotor 30 ′ of the screw compressor during one gas-supply process is the central angle corresponding to the distance d 1 +a 1 which the rotor end rotates along as shown in FIG. 4 .
- d 1 is the width of the gas-supply hole 10 ′.
- a 1 is the distance between teeth end spiral lines of two adjacent rotor teeth 301 ′, 302 ′, corresponding to a rotation angle of the screw channel 60 ′.
- the rotation angle for gas supply along the radial direction is always larger than the rotation angle of the screw channel 60 ′.
- the disadvantages of the radially-arranged gas-supply hole 10 ′ of an economizer is: the time for a complete gas-supply process of the screw compressor is too long, thus may cause potential backflow, and then cause a series of bad results of influencing the performances of the screw compressor, vibration of pipes, generating high temperature at gas-supply hole area, and high noises etc.
- an object of the present invention is to provide a screw compressor which is capable of supplying gaseous refrigerating working medium to a compressor cavity in shorter time for eliminating or reducing potential backflow of airflow.
- a screw compressor adapted for connecting with an economizer for gas supply, comprises a main body defining a compressor cavity, a male rotor and a female rotor received in the compressor cavity, a gas-vent base defining at least one gas-supply hole therein adapted for communicating with said economizer.
- the male rotor and the female rotor are parallel to and meshed with each other.
- At least the male rotor comprises at least two teeth defining at least one tooth channel therebetween.
- the gas-supply hole is axially aligned with the at least one tooth channel to let gas from the economizer pass therethrough and enter into the at least one tooth channel along the axial direction of the male rotor.
- FIG. 1A is a schematic view of a conventional refrigerating cycle system with a heat-exchange type economizer
- FIG. 1B is a Pressure-Enthalpy diagram of the refrigerating cycle system with a heat-exchange type economizer
- FIG. 2A is a schematic view of a conventional refrigerating cycle system with a flash-type economizer
- FIG. 2B is a Pressure-Enthalpy diagram of the refrigerating cycle system with a flash-type economizer
- FIG. 3 is a view illustrating a radially-arranged gas-supply hole of a conventional economizer and a male rotor
- FIG. 4 is a schematic view illustrating a gas supply process of the conventional economizer with a radially-arranged gas-supply hole
- FIG. 5 is a view illustrating outer contour of a gas-supply hole of a screw compressor in accordance with a first embodiment of the present invention
- FIG. 6 is a view illustrating outer contour of a gas-supply hole of the screw compressor in accordance with a second embodiment of the present invention.
- FIG. 7 is a schematic view illustrating that a tooth channel of a male rotor is separated from the gas-supply hole
- FIG. 8 is a schematic view illustrating that the tooth channel of the male rotor is going to be communicated with the gas-supply hole
- FIG. 9 is a schematic view illustrating that the tooth channel of the male rotor communicates with the gas-supply hole
- FIG. 10 is a schematic view illustrating that the tooth channel of the male rotor passes away from the gas-supply hole
- FIG. 11 is a view illustrating the rotating distance of the male rotor during one gas supply process of an economizer of the screw compressor of the present invention
- FIG. 12 is a partially assembled view of the screw compressor in accordance with the present invention.
- FIG. 13 is a schematic view illustrating the exact location of the gas-supply hole in the screw compressor in accordance with the present invention.
- a screw compressor 100 in accordance with the present invention comprises a main body 20 , a gas-vent base 50 at one end of the main body 20 , a male rotor 30 and a female rotor 40 parallel to and meshed with each other. Both the male rotor 30 and the female rotor 40 are received in the main body 20 with one end face 305 thereof facing to the gas-vent base 50 .
- the screw compressor 100 also comprises an economizer (not labeled) defined with at least one gas-supply hole 10 in the gas vent base 50 of the screw compressor 100 .
- the economizer supplies gas to the screw compressor 100 along an axial direction and through the end face 305 of the male rotor 30 .
- the screw compressor 100 is a dual-screw compressor or a triple-screw compressor. However, it should be understood that in alternative embodiments, other screw compressors are also available.
- the gas-supply hole 10 in accordance with a first embodiment of the present invention is substantially of triple-angle and has an outer contour consistent with tooth shape, and tooth root circle of the male rotor 30 .
- the gas-supply hole 10 comprises opposite arc-shape first and second lateral boundaries 101 , 102 and an arc-shape bottom boundary 103 connecting with the lateral boundaries 101 , 102 .
- the opposite first and second lateral boundaries 101 , 102 of the gas-supply hole 10 anastomose with part of the two opposite first and second lateral edges 303 , 304 of the male rotor 30 .
- the majority of the first lateral boundary 101 anastomoses with corresponding part of the first lateral edge 303 .
- the second lateral edge 304 of the male rotor 30 rotates to be close to the second lateral boundary 102 to communicate with the gas-supply hole 10 for gas supply, the majority of the second lateral boundary 102 anastomoses with corresponding part of the second lateral edge 304 .
- the majority of the bottom boundary 103 of the gas-supply hole 10 anastomoses with tooth boot arc of the male rotor 30 .
- the gas-supply hole 10 also could have alternative shapes, such as a substantial circle, rectangular shape, or a flat bar shape et al. according to the tooth shape of the male rotor 30 . As shown in FIG. 6 , the gas-supply hole 10 comprises a pair of straight-line first and second lateral boundaries 101 , 102 and an arc-shape bottom boundary 103 .
- the economizer also could be equipped with a plurality of gas-supply holes 10 defined in the gas-vent base 50 symmetrically or asymmetrically.
- the gas supply process includes steps as follows:
- the male rotor 30 rotates along an anticlockwise direction with the second lateral edge 304 of the first tooth 301 substantially anastomosing with the second lateral boundary 102 of the gas-supply hole 10 to be ready to communicate with the gas-supply hole 10 for gas supply (as shown in FIG. 8 );
- the rotation angle a of the male rotor 30 (first angle) is always smaller than the rotation angle a 1 (second angle) of the tooth channel 60 in the condition that the area of the gas-supply hole 10 is no bigger than that of the tooth channel 60 of the male rotor 30 .
- the present invention provides gas supply in an axial direction which is capable of supplying gas to a compressor cavity (not labeled) in the shortest time for optimizing performances of the screw compressor 100 .
- the screw compressor 100 of the present invention is capable of feeding gaseous refrigerating working medium into the compressor cavity in a shorter time for eliminating or reducing potential backflow, hence optimizing the performances of the economizer artificially.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A screw compressor for connecting with an economizer for gas supply, includes a main body defining a compressor cavity, a male rotor and a female rotor received in the compressor cavity, a gas-vent base defining at least one gas-supply hole therein adapted for communicating with the economizer. The male rotor and the female rotor are parallel to and meshed with each other. At least the male rotor includes at least two teeth defining at least one tooth channel therebetween. The gas-supply hole is axially aligned with the at least one tooth channel to let gas from the economizer pass therethrough and enter into the at least one tooth channel along the axial direction of the male rotor.
Description
- The present invention relates to a screw compressor, more particularly to a screw compressor with economizer.
- A screw compressor is one of the most common types of rotary compressors and comprises a pair of parallel, meshed male and female rotors. To improve the efficiency of a compressor, an energy-saving cycle system with an economizer is often utilized. Please refer to
FIGS. 1A-2B , refrigeratingcycle Systems 100′, 100″ are illustrated.FIG. 1A is a schematic view of the refrigeratingcycle system 100′ with a heat-exchange type economizer 3′. The refrigeratingcycle system 100′ consists of acompressor 6′ connecting with a condenser 1′, an evaporator 5′ and the heat-exchange type economizer 3′.FIG. 1B is a Pressure-Enthalpy diagram of the refrigeratingcycle system 100′ with the heat-exchange type economizer 3′. -
FIG. 2A is a schematic view of the refrigeratingcycle system 100″ with a flash-type economizer 3″ andFIG. 2B is a Pressure-Enthalpy diagram of the refrigeratingcycle system 100″ with the flash-type economizer 3″. The refrigeratingcycle system 100″ consists of acompressor 6″ connecting with a condenser 1″, an evaporator 5″ and the heat-exchange type economizer 3″. - Please refer to
FIG. 3 , a gas-supply hole 10′ of an economizer of the conventional screw compressor is arranged along a radial direction to communicate with atooth channel 60′ from time to time for gas supply. Thetooth channel 60′ is defined by twoadjacent teeth 301′, 302′ of amale rotor 30′. -
FIG. 4 illustrates a gas-supply process of the conventional radially-arranged gas-supply hole 10′ of the economizer. The rotating angle of therotor 30′ of the screw compressor during one gas-supply process (along the arrow direction shown inFIG. 4 ) is the central angle corresponding to the distance d1+a1 which the rotor end rotates along as shown inFIG. 4 . d1 is the width of the gas-supply hole 10′. a1 is the distance between teeth end spiral lines of twoadjacent rotor teeth 301′, 302′, corresponding to a rotation angle of thescrew channel 60′. Hence, it is obvious that the rotation angle for gas supply along the radial direction is always larger than the rotation angle of thescrew channel 60′. - The disadvantages of the radially-arranged gas-
supply hole 10′ of an economizer is: the time for a complete gas-supply process of the screw compressor is too long, thus may cause potential backflow, and then cause a series of bad results of influencing the performances of the screw compressor, vibration of pipes, generating high temperature at gas-supply hole area, and high noises etc. - Accordingly, an object of the present invention is to provide a screw compressor which is capable of supplying gaseous refrigerating working medium to a compressor cavity in shorter time for eliminating or reducing potential backflow of airflow.
- In order to achieve the above-mentioned object, a screw compressor adapted for connecting with an economizer for gas supply, comprises a main body defining a compressor cavity, a male rotor and a female rotor received in the compressor cavity, a gas-vent base defining at least one gas-supply hole therein adapted for communicating with said economizer. The male rotor and the female rotor are parallel to and meshed with each other. At least the male rotor comprises at least two teeth defining at least one tooth channel therebetween. The gas-supply hole is axially aligned with the at least one tooth channel to let gas from the economizer pass therethrough and enter into the at least one tooth channel along the axial direction of the male rotor.
- The foregoing has outlined rather broadly the features and technical advantages of the present invention in order that the detailed description of the invention that follows may be better understood. Additional features and advantages of the invention will be described hereinafter, which form the subject of the claims of the invention.
- For a more complete understanding of the present invention, and the advantages thereof, reference is now made to the following descriptions taken in conjunction with the accompanying drawings, in which:
-
FIG. 1A is a schematic view of a conventional refrigerating cycle system with a heat-exchange type economizer; -
FIG. 1B is a Pressure-Enthalpy diagram of the refrigerating cycle system with a heat-exchange type economizer; -
FIG. 2A is a schematic view of a conventional refrigerating cycle system with a flash-type economizer; -
FIG. 2B is a Pressure-Enthalpy diagram of the refrigerating cycle system with a flash-type economizer; -
FIG. 3 is a view illustrating a radially-arranged gas-supply hole of a conventional economizer and a male rotor; -
FIG. 4 is a schematic view illustrating a gas supply process of the conventional economizer with a radially-arranged gas-supply hole; -
FIG. 5 is a view illustrating outer contour of a gas-supply hole of a screw compressor in accordance with a first embodiment of the present invention; -
FIG. 6 is a view illustrating outer contour of a gas-supply hole of the screw compressor in accordance with a second embodiment of the present invention; -
FIG. 7 is a schematic view illustrating that a tooth channel of a male rotor is separated from the gas-supply hole; -
FIG. 8 is a schematic view illustrating that the tooth channel of the male rotor is going to be communicated with the gas-supply hole; -
FIG. 9 is a schematic view illustrating that the tooth channel of the male rotor communicates with the gas-supply hole; -
FIG. 10 is a schematic view illustrating that the tooth channel of the male rotor passes away from the gas-supply hole; -
FIG. 11 is a view illustrating the rotating distance of the male rotor during one gas supply process of an economizer of the screw compressor of the present invention; -
FIG. 12 is a partially assembled view of the screw compressor in accordance with the present invention; -
FIG. 13 is a schematic view illustrating the exact location of the gas-supply hole in the screw compressor in accordance with the present invention. - In the following description, numerous specific details are set forth to provide a thorough understanding of the present invention. However, it will be obvious to those skilled in the art that the present invention may be practiced without such specific details. In other instances, well-known circuits have been shown in block diagram form in order not to obscure the present invention in unnecessary detail. For the most part, details concerning timing considerations and the like have been omitted inasmuch as such details are not necessary to obtain a complete understanding of the present invention and are within the skills of persons of ordinary skill in the relevant art.
- Reference will be made to the drawing figures to describe the present invention in detail, wherein depicted elements are not necessarily shown to scale and wherein like or similar elements are designated by same or similar reference numeral through the several views and same or similar terminology.
- Please refer to
FIGS. 12-13 , ascrew compressor 100 in accordance with the present invention comprises amain body 20, a gas-vent base 50 at one end of themain body 20, amale rotor 30 and afemale rotor 40 parallel to and meshed with each other. Both themale rotor 30 and thefemale rotor 40 are received in themain body 20 with oneend face 305 thereof facing to the gas-vent base 50. Thescrew compressor 100 also comprises an economizer (not labeled) defined with at least one gas-supply hole 10 in thegas vent base 50 of thescrew compressor 100. The economizer supplies gas to thescrew compressor 100 along an axial direction and through theend face 305 of themale rotor 30. In the preferred embodiment, thescrew compressor 100 is a dual-screw compressor or a triple-screw compressor. However, it should be understood that in alternative embodiments, other screw compressors are also available. - Please refer to
FIG. 5 , the gas-supply hole 10 in accordance with a first embodiment of the present invention is substantially of triple-angle and has an outer contour consistent with tooth shape, and tooth root circle of themale rotor 30. The gas-supply hole 10 comprises opposite arc-shape first and secondlateral boundaries lateral boundaries lateral boundaries supply hole 10 anastomose with part of the two opposite first and secondlateral edges male rotor 30. Therefore, when the firstlateral edge 303 of themale rotor 30 rotates to be close to the firstlateral boundary 101 to separate from the gas-supply hole 10, the majority of the firstlateral boundary 101 anastomoses with corresponding part of the firstlateral edge 303. When the secondlateral edge 304 of themale rotor 30 rotates to be close to the secondlateral boundary 102 to communicate with the gas-supply hole 10 for gas supply, the majority of the secondlateral boundary 102 anastomoses with corresponding part of the secondlateral edge 304. The majority of the bottom boundary 103 of the gas-supply hole 10 anastomoses with tooth boot arc of themale rotor 30. - The gas-
supply hole 10 also could have alternative shapes, such as a substantial circle, rectangular shape, or a flat bar shape et al. according to the tooth shape of themale rotor 30. As shown inFIG. 6 , the gas-supply hole 10 comprises a pair of straight-line first and secondlateral boundaries - The economizer also could be equipped with a plurality of gas-
supply holes 10 defined in the gas-vent base 50 symmetrically or asymmetrically. - The gas supply process includes steps as follows:
- S1) As shown in
FIG. 7 , onetooth channel 60 defined by two adjacent first andsecond teeth male rotor 30 separates from the gas-supply hole 10, and the gas-supply hole 10 is aligning with one tooth=301; - S2) the
male rotor 30 rotates along an anticlockwise direction with the secondlateral edge 304 of thefirst tooth 301 substantially anastomosing with the secondlateral boundary 102 of the gas-supply hole 10 to be ready to communicate with the gas-supply hole 10 for gas supply (as shown inFIG. 8 ); - S3) the
male rotor 30 continues rotating along the anticlockwise direction, and thetooth channel 60 becomes communicating with the gas-supply hole 10 until reaching the largest area for gas supply (as shown inFIG. 9 ); - S4) then the
male rotor 30 continues rotating with the firstlateral edge 303 of thesecond tooth 302 substantially anastomosing with the firstlateral boundary 101 of the gas-supply hole 10, the gas supply process this time finishes (as shown inFIG. 10 ). - S5) turning to S1 to repeat S1 to S4 until the whole gas supply process finishes.
- Please refer to
FIG. 11 , since the gas supply to themale rotor 30 is conducted from an end face 501 of the gas-vent base 50, that is feeding gas axially, the rotation angle a of the male rotor 30 (first angle) is always smaller than the rotation angle a1 (second angle) of thetooth channel 60 in the condition that the area of the gas-supply hole 10 is no bigger than that of thetooth channel 60 of themale rotor 30. Compared with the conventional radially-arranged gas-supply hole 10′ (the rotation angle of themale rotor 30′ is always bigger than the rotation angle al of atooth channel 60′.), the present invention provides gas supply in an axial direction which is capable of supplying gas to a compressor cavity (not labeled) in the shortest time for optimizing performances of thescrew compressor 100. - In summary, the
screw compressor 100 of the present invention is capable of feeding gaseous refrigerating working medium into the compressor cavity in a shorter time for eliminating or reducing potential backflow, hence optimizing the performances of the economizer artificially. - It is to be understood, however, that even though numerous characteristics and advantages of the present invention have been set forth in the foregoing description, together with details of the structure and function of the invention, the disclosure is illustrative only, and changes may be made in detail, especially in matters of shape, size, and arrangement of parts within the principles of the invention to the full extent indicated by the broad general meaning of the terms in which the appended claims are expressed. For example, the tongue portion is extended in its length or is arranged on a reverse side thereof opposite to the supporting side with other contacts but still holding the contacts with an arrangement indicated by the broad general meaning of the terms in which the appended claims are expressed.
Claims (11)
1. A screw compressor adapted for connecting with an economizer for gas supply, comprising:
a main body defining a compressor cavity;
a male rotor and a female rotor received in the compressor cavity, the male rotor and the female rotor meshed with each other, and at least the male rotor comprising at least two teeth defining at least one tooth channel therebetween;
a gas-vent base defining at least one gas-supply hole therein adapted for communicating with said economizer; and wherein the gas-supply hole is axially aligned with the at least one tooth channel to let gas from the economizer pass therethrough and enter into the at least one tooth channel along the axial direction of the male rotor.
2. The screw compressor as claimed in claim 1 , wherein the outer contour of the gas-supply hole is similar to that of the tooth of the male rotor.
3. The screw compressor as claimed in claim 2 , wherein the area of the gas-supply hole is no larger than that of the tooth.
4. The screw compressor as claimed in claim 1 , wherein the gas-supply hole rotates at a first angle, while the male rotor rotates at a second angle of the at least tooth channel, and wherein the first angle of the gas-supply hole is always smaller than the second angle of the at least one tooth channel.
5. The screw compressor as claimed in claim 1 , wherein the gas-supply hole comprises first and second lateral boundaries and a bottom boundary connecting with the first and second lateral boundaries, and the tooth of the male rotor comprises first and second lateral edges, and wherein as the male rotor rotates, the first and second lateral boundaries of the gas-supply hole is capable of partially anastomosing with the first and second lateral edges of the male rotor.
6. The screw compressor as claimed in claim 1 , wherein the gas-supply hole has at least one of the shapes of triangle, circle, rectangular, flat bar.
7. The screw compressor as claimed in claim 1 , wherein the gas-vent base defines a plurality of gas-supply holes therethrough to communicate with said economizer and the at least one tooth channel of the male rotor.
8. The screw compressor as claimed in claim 1 , wherein the screw compressor is a dual-screw compressor.
9. The screw compressor as claimed in claim 1 , wherein the screw compressor is a triple-screw compressor.
10. The screw compressor as claimed in claim 5 , wherein the at least two teeth of the male rotor comprises a first tooth and a second tooth, and wherein before the gas-supply hole communicates with the at least one tooth channel, the male rotor rotates to such a position that the second lateral boundary of the gas-supply hole partially anastomoses with the second lateral edge of the first tooth.
11. The screw compressor as claimed in claim 10 , wherein as the gas-supply hole is going to separate from the at least one tooth channel, the male rotor rotates to such a position that the first lateral boundary of the gas-supply hole partially anastomoses with the first lateral edge of the second tooth.
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
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CN20101056279.4 | 2010-04-26 | ||
CN201010156279 | 2010-04-26 | ||
CN2010105425404A CN101979880B (en) | 2010-04-26 | 2010-11-02 | Screw compressor |
CN2010542540.4 | 2010-11-02 | ||
PCT/CN2010/079353 WO2011134261A1 (en) | 2010-04-26 | 2010-12-01 | Screw compressor |
Publications (1)
Publication Number | Publication Date |
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US20120058001A1 true US20120058001A1 (en) | 2012-03-08 |
Family
ID=43600405
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US13/148,943 Abandoned US20120058001A1 (en) | 2010-04-26 | 2010-12-01 | Screw compressor with economizer |
Country Status (4)
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US (1) | US20120058001A1 (en) |
EP (1) | EP2565456B1 (en) |
CN (2) | CN201836053U (en) |
WO (1) | WO2011134261A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN201836053U (en) * | 2010-04-26 | 2011-05-18 | 上海维尔泰克螺杆机械有限公司 | Screw rod compressor |
JP5871578B2 (en) * | 2011-11-17 | 2016-03-01 | 三菱電機株式会社 | Screw compressor |
CN106401965B (en) * | 2016-06-24 | 2019-03-22 | 珠海格力电器股份有限公司 | A kind of exhaust bearing block and helical-lobe compressor |
CN106949051B (en) | 2017-03-20 | 2018-11-30 | 珠海格力电器股份有限公司 | Compressor slide valve and helical-lobe compressor with it |
CN106979160A (en) * | 2017-04-26 | 2017-07-25 | 珠海格力电器股份有限公司 | Helical-lobe compressor, air-conditioning device and refrigerating plant |
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US6638042B1 (en) * | 2002-05-08 | 2003-10-28 | Carrier Corporation | Asymmetric porting for multi-rotor screw compressor |
JP2008297996A (en) * | 2007-05-31 | 2008-12-11 | Mayekawa Mfg Co Ltd | Single screw type multiple stage compressor and freezing-refrigerating system using same |
US20100229595A1 (en) * | 2007-06-11 | 2010-09-16 | Daikin Industries, Ltd. | Compressor and refrigerating apparatus |
US7802974B2 (en) * | 2004-09-30 | 2010-09-28 | Carrier Corporation | Screw compressor having asymmetric seal around rotor axis |
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CN1007076B (en) * | 1987-02-27 | 1990-03-07 | 武汉冷冻机厂 | Exhaust end base of oil injection threaded bolt refrigerating compressor |
US5775117A (en) * | 1995-10-30 | 1998-07-07 | Shaw; David N. | Variable capacity vapor compression cooling system |
JP2001176534A (en) * | 1999-12-17 | 2001-06-29 | Toyota Autom Loom Works Ltd | Air supply device for fuel cell |
US7156624B2 (en) * | 2004-12-09 | 2007-01-02 | Carrier Corporation | Compressor sound suppression |
CN201344131Y (en) * | 2009-01-22 | 2009-11-11 | 中国船舶重工集团公司第七一一研究所 | Air exhaust end seat with variable internal compression ratio for screw compressor |
CN101581303A (en) * | 2009-06-15 | 2009-11-18 | 大连冷冻机股份有限公司 | Screw type refrigerating compressor for ship |
CN101581302A (en) * | 2009-06-15 | 2009-11-18 | 大连冷冻机股份有限公司 | Hydrojet cooling screw type refrigerating compressor set for ship |
CN201836053U (en) * | 2010-04-26 | 2011-05-18 | 上海维尔泰克螺杆机械有限公司 | Screw rod compressor |
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2010
- 2010-11-02 CN CN2010206010451U patent/CN201836053U/en not_active Expired - Lifetime
- 2010-11-02 CN CN2010105425404A patent/CN101979880B/en active Active
- 2010-12-01 WO PCT/CN2010/079353 patent/WO2011134261A1/en active Application Filing
- 2010-12-01 EP EP10850592.6A patent/EP2565456B1/en active Active
- 2010-12-01 US US13/148,943 patent/US20120058001A1/en not_active Abandoned
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Also Published As
Publication number | Publication date |
---|---|
CN201836053U (en) | 2011-05-18 |
CN101979880B (en) | 2013-07-31 |
CN101979880A (en) | 2011-02-23 |
WO2011134261A1 (en) | 2011-11-03 |
EP2565456A4 (en) | 2017-05-17 |
EP2565456A1 (en) | 2013-03-06 |
EP2565456B1 (en) | 2018-08-01 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SHANGHAI POWER TECH. SCREW MACHINERY CO., LTD., CH Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:TANG, YAN;REEL/FRAME:026731/0604 Effective date: 20110726 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |