CN115507025B - High rotor axial temperature uniformity twin-screw compressor - Google Patents
High rotor axial temperature uniformity twin-screw compressor Download PDFInfo
- Publication number
- CN115507025B CN115507025B CN202211274706.8A CN202211274706A CN115507025B CN 115507025 B CN115507025 B CN 115507025B CN 202211274706 A CN202211274706 A CN 202211274706A CN 115507025 B CN115507025 B CN 115507025B
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- China
- Prior art keywords
- liquid supply
- liquid
- supply chamber
- rotor
- suction end
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- 239000007788 liquid Substances 0.000 claims abstract description 183
- 230000001105 regulatory effect Effects 0.000 claims description 7
- 238000009434 installation Methods 0.000 claims description 5
- 238000001816 cooling Methods 0.000 description 4
- 230000001050 lubricating effect Effects 0.000 description 4
- 238000005461 lubrication Methods 0.000 description 4
- 239000003921 oil Substances 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
Abstract
The invention discloses a high rotor axial temperature uniformity double-screw compressor, which comprises a compressor body and a liquid supply system, wherein a suction end liquid supply chamber and a discharge end liquid supply chamber which are concentric with a rotor shaft are arranged among a suction end bearing cavity, a discharge end bearing cavity and a working cavity of the compressor body, and the liquid supply system comprises a branch pipeline for injecting medium-temperature liquid into the suction end liquid supply chamber and a branch pipeline for injecting low-temperature liquid into the discharge end bearing cavity or the discharge end liquid supply chamber. The invention realizes the control of the thermal boundary conditions at the two ends of the rotor by using the medium-temperature liquid and the low-temperature liquid, thereby improving the performance of the double-screw compressor.
Description
Technical Field
The invention belongs to the technical field of compressors, relates to a liquid supply technology for improving the performance of a double-screw compressor, and in particular relates to a method for improving the uniformity of the axial temperature distribution of a rotor (namely the axial temperature uniformity of the rotor) when the double-screw compressor operates.
Background
The double-screw compressor is widely applied to industries such as refrigeration, air compression, petrochemical industry and the like due to the advantages of high reliability, high efficiency, convenient operation, strong adaptability, low maintenance cost and the like under medium and low pressure working conditions. The rotor is used as a core component of the double-screw compressor, and the design of the end surface molded line and the gap of the rotor determines the overall performance of the double-screw compressor. The clearance design of the rotors refers to correcting the theoretical rotor end surface molded lines by analyzing the stress deformation and the thermal expansion of the rotors in the operation process of the double-screw compressor, so that the female and male rotors processed according to the corrected actual rotor end surface molded lines contain certain clearances between the rotors and the working cavity, and the reliable operation of the rotors of the double-screw compressor is ensured.
The rotor axial temperature of the twin-screw compressor is gradually increased from the air suction end face to the air discharge end face during operation due to the influence of the gas temperature distribution of the working cavity, and the corresponding clearance is gradually reduced from the air suction end face to the air discharge end face. Therefore, the clearance design of the rotor is often used as a reference for the thermal expansion condition of the rotor at the exhaust end face, so as to avoid the situation of rotor seizure caused by too small clearance of the rotor close to the exhaust end face. However, this also makes the clearance of the rotor near the suction end face of the twin-screw compressor often too large during operation, resulting in deterioration of the twin-screw compressor performance, particularly with regard to the performance of dry oil-free twin-screw compressors.
The liquid supply system of the twin-screw compressor is generally used for lubricating the bearing cavity and the rotor in the compressor body, and simultaneously plays a role in sealing and cooling the compressed gas in the working cavity. In some compressors, for example CN205714761U, CN105927548A, a sealed chamber is provided into which a liquid (oil, water) can be injected. However, the cooling, lubricating and sealing liquid adopted at the suction end and the discharge end of the compressor at present has no effect on realizing the axial temperature uniformity of the rotor.
Disclosure of Invention
The invention aims to provide a double-screw compressor with high rotor axial temperature uniformity.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
the double-screw compressor comprises a compressor body and a liquid supply system, wherein the compressor body comprises a rotor (the rotor refers to any one of a female rotor and a male rotor of the double-screw compressor), a working cavity, a suction end bearing cavity penetrated by one end of the rotor extending out of the working cavity and a discharge end bearing cavity penetrated by the other end of the rotor extending out of the working cavity (namely, one end of a rotor shaft penetrates the suction end bearing cavity and the other end of the rotor shaft penetrates the discharge end bearing cavity), a suction end liquid supply chamber positioned outside the rotor is arranged between the suction end bearing cavity and the working cavity, and the liquid supply system comprises a cooler, an inlet main pipeline for supplying high-temperature liquid, an outlet main pipeline for supplying low-temperature liquid and a suction end branch pipeline for injecting the high-temperature liquid drained from the inlet main pipeline and the low-temperature liquid drained from the outlet main pipeline into the suction end liquid supply chamber, wherein the inlet main pipeline and the outlet main pipeline are respectively connected with the cooler (namely, the inlet main pipeline is connected with an inlet of the cooler, and the outlet main pipeline is connected with an outlet of the cooler).
Preferably, the compressor body further includes an annular groove for forming a suction end liquid supply chamber in cooperation with the rotor, the suction end liquid supply chamber and the suction end bearing chamber are communicated through a minute installation gap of the rotor (specifically, a portion of the rotor shaft near a suction end face of the working chamber) in the compressor body (specifically, a chamber for communicating the working chamber and the suction end bearing chamber and allowing a corresponding portion of the rotor shaft to pass through), and the suction end liquid supply chamber and the working chamber are also communicated through the minute installation gap.
Preferably, an inlet bypass pipeline is arranged on the inlet main pipeline, an outlet bypass pipeline is arranged on the outlet main pipeline, and the inlet bypass pipeline and the outlet bypass pipeline are respectively connected with the air suction end branch pipeline, so that medium-temperature liquid can be injected into the air suction end liquid supply chamber from the outside of the compressor body through the air suction end branch pipeline.
Preferably, the inlet bypass pipeline and the outlet bypass pipeline are respectively provided with a flow regulating valve element.
Preferably, the compressor body further comprises an air suction end liquid inlet hole for communicating the air suction end branch pipeline with the air suction end liquid supply chamber.
Preferably, the compressor body further comprises a suction end liquid supply chamber liquid return hole for leading out liquid from the suction end liquid supply chamber, and the led-out liquid can finally flow to the working cavity or the inlet main pipeline.
Preferably, the aperture of the liquid return hole of the liquid supply chamber at the air suction end is smaller than the aperture of the liquid inlet hole at the air suction end.
Preferably, the compressor body further includes an annular groove for forming an exhaust-end liquid supply chamber (located between the exhaust-end bearing chamber and the working chamber and located outside the rotor) with the rotor through cooperation, the exhaust-end liquid supply chamber and the exhaust-end bearing chamber are communicated through a tiny installation gap of the rotor (specifically, a portion of the rotor shaft close to an exhaust end face of the working chamber) in the compressor body (specifically, a cavity for communicating the working chamber and the exhaust-end bearing chamber and allowing a corresponding portion of the rotor shaft to pass through), and the exhaust-end liquid supply chamber and the working chamber are also communicated through the tiny installation gap.
Preferably, the liquid supply system further includes an exhaust end branch pipe, one end of the exhaust end branch pipe is connected to the outlet main pipe, and the other end of the exhaust end branch pipe is connected to the exhaust end bearing chamber or the exhaust end liquid supply chamber (when the exhaust end liquid supply chamber is provided, the exhaust end branch pipe is connected to the exhaust end liquid supply chamber), so that low-temperature liquid can be injected into the exhaust end bearing chamber or the exhaust end liquid supply chamber from the outside of the compressor body through the exhaust end branch pipe.
Preferably, the compressor body further comprises an exhaust end liquid inlet hole for communicating the exhaust end branch pipeline with the exhaust end liquid supply chamber or the exhaust end bearing cavity.
Preferably, the compressor body further comprises an exhaust end liquid supply chamber liquid return hole for leading out liquid from the exhaust end liquid supply chamber, and the led-out liquid can finally flow to the working cavity or the inlet main pipeline.
Preferably, a shaft seal is arranged between the suction end liquid supply chamber and the working cavity, or shaft seals are arranged between the suction end liquid supply chamber and the working cavity and between the exhaust end liquid supply chamber and the working cavity.
Preferably, the liquid in the inlet main line and the outlet main line is lubricating oil, water or other lubricating and cooling medium.
The beneficial effects of the invention are as follows:
according to the invention, the medium-temperature liquid is formed by utilizing the liquid led out from the inlet main pipeline and the outlet main pipeline in the liquid self-supply system through the liquid supply chamber at the air suction end, and the problem that the gap between the rotor and the air suction end face is larger due to uneven axial temperature distribution of the rotor is solved by effectively utilizing the lifting of the liquid supply temperature, so that the performance of the double-screw compressor is improved.
Furthermore, the invention simultaneously sets the liquid supply chamber at the air suction end and the liquid supply chamber at the air discharge end, and improves the axial temperature uniformity of the rotor when the double-screw compressor operates and improves the uniformity of the distribution of each gap when the rotor operates by controlling the thermal boundary conditions at the two ends of the rotor through the medium-temperature liquid and the low-temperature liquid which are supplied.
Furthermore, the applicability of the double-screw compressor in engineering application is improved through the flow regulating valve element on the bypass pipe at two sides of the cooler.
Drawings
Fig. 1 is a schematic structural view (male rotor side) of a twin screw compressor in embodiment 1 of the present invention;
fig. 2 is a schematic structural view (male rotor side) of a twin screw compressor in embodiment 2 of the present invention;
fig. 3 is a schematic structural view (male rotor side) of a twin screw compressor in embodiment 3 of the present invention;
FIG. 4 is a cross-sectional view of the male rotor side liquid supply chamber of the twin screw compressor in example 1 of the present invention;
in the figure: 1-compressor body (outlined by dotted line), 2-liquid supply system (outlined by dot-dash line), 3-suction end bearing cavity, 4-working cavity, 5-suction end liquid supply chamber, 6-suction end liquid inlet hole, 7-suction end liquid supply chamber liquid return hole, 8-branch pipe for supplying medium temperature liquid, 9-exhaust end bearing cavity, 10-branch pipe for supplying low temperature liquid, 11-cooler, 12-inlet main pipe, 13-outlet main pipe, 14-inlet bypass pipe, 15-outlet bypass pipe, 16-three-way joint, 17-flow regulating valve, 18-shaft seal, 19-rotor shaft, 20-exhaust end liquid inlet hole, 21-exhaust end liquid supply chamber, 22-exhaust end liquid supply chamber liquid return hole.
Detailed Description
The present invention will now be described in further detail with reference to the accompanying drawings and examples which are given solely for the purpose of illustration and are not intended to limit the scope of the invention.
Example 1
Referring to fig. 1, the twin-screw compressor provided in this embodiment includes a compressor body 1 (including a casing, and a working chamber 4, a bearing chamber, a female rotor, and a male rotor located in the casing), and a liquid supply system 2, where lubrication and cooling media adopted by the liquid supply system 2 are lubricating oil, and the two rotors are disposed in the casing of the compressor body 1 in the same manner (such as a bearing for supporting the rotors in the bearing chamber, lubrication in the bearing chamber, and a liquid return structure of the bearing chamber), and a structure and a principle for obtaining high axial uniformity of temperature of the rotors are described below with the male rotor as a representative.
An annular groove (concentric with the rotor shaft 19, see fig. 4) for forming a suction end liquid supply chamber 5 (located in the casing of the compressor body 1) is formed between the working chamber 4 of the compressor body 1 and the suction end bearing chamber 3 (the suction end bearing chamber 3 is internally provided with a bearing for supporting one end of the rotor shaft 19 near the suction end face of the working chamber 4), and the casing of the compressor body 1 is provided with a suction end liquid inlet hole 6 and a suction end liquid supply chamber liquid return hole 7 which are communicated with the suction end liquid supply chamber 5. The liquid supply system 2 comprises a branch pipe 8 for supplying medium-temperature liquid to the liquid supply chamber 5 at the air suction end and a branch pipe 10 for supplying low-temperature liquid to the bearing chamber 9 at the air discharge end of the compressor body 1 (the bearing chamber 9 at the air discharge end is internally provided with a bearing for supporting the rotor shaft 19 near the air discharge end face of the working chamber 4), the branch pipe 8 for supplying medium-temperature liquid is connected with the liquid inlet hole 6 at the air suction end, the shell of the compressor body 1 is also provided with the liquid inlet hole 20 at the air discharge end communicated with the bearing chamber 9 at the air discharge end, and the branch pipe 10 for supplying low-temperature liquid is connected with the liquid inlet hole 20 at the air discharge end.
The liquid supply system 2 further comprises a cooler 11, an inlet main pipeline 12 and an outlet main pipeline 13 which are connected with the cooler 11, wherein high-temperature liquid in the inlet main pipeline 12 is from a gas-liquid separator of exhaust of a compressor (working cavity 4), is cooled into low-temperature liquid by the cooler 11, and then enters the outlet main pipeline 13. The low-temperature liquid in the outlet main pipeline 13 flows to the working chamber 4 and is used for sealing and cooling the gas in the working chamber 4. The outlet main line 13 is also connected to said branch line 10 for supplying cryogenic liquid, thereby providing cryogenic liquid.
An inlet bypass line 14 is connected to the inlet main line 12 (one end of the inlet bypass line 14 is connected to the inlet main line 12), an outlet bypass line 15 is connected to the outlet main line 13 (one end of the outlet bypass line 15 is connected to the outlet main line 13), and the other ends of the inlet bypass line 14 and the outlet bypass line 15 are connected to the branch line 8 for supplying the medium temperature liquid via a three-way joint 16. The inlet bypass pipeline 14 and the outlet bypass pipeline 15 are provided with flow regulating valve elements 17, and the liquid supply temperature of the liquid supply chamber 5 at the air suction end can be controlled by regulating the flow regulating valve elements 17, so that the differential control of the thermal boundary conditions at the two ends of the rotor can be realized aiming at different working conditions, and the uniformity of the distribution of each gap between the air suction end face and the air discharge end face during the operation of the rotor is improved.
The part of the suction end liquid supply chamber 5, which is close to the suction end surface of the working chamber 4, is communicated with a micro gap between the working chamber 4 and the cavity of the suction end bearing chamber 3 (the annular groove of the suction end liquid supply chamber 5 is arranged on the inner wall of the cavity) in the shell of the compressor body 1 through the rotor shaft 19. The aperture of the liquid return hole 7 of the liquid supply chamber at the air suction end on the compressor body 1 is smaller than the aperture of the liquid inlet hole 6 at the air suction end, so that the flow of the liquid return hole 7 of the liquid supply chamber at the air suction end is smaller than the flow of the liquid inlet hole 6 at the air suction end, and the lubrication oil quantity of the bearing is ensured (the larger the difference between the flow of the liquid return hole 7 of the liquid supply chamber at the air suction end and the flow of the liquid inlet hole 6 at the air suction end is, the larger the lubrication oil quantity of the bearing in the bearing cavity 3 at the air suction end is).
The liquid discharged from the liquid return hole 7 of the liquid supply chamber at the suction end flows to the working cavity 4.
Example 2
The twin screw compressor of this embodiment is used in a dry oil-free application, considering that the suction side liquid supply chamber 5 and the working chamber 4 in embodiment 1 can also communicate with each other through the minute gap. The present embodiment differs from the twin screw compressor of embodiment 1 in that:
referring to fig. 2, the suction side liquid supply chamber 5 is provided with a shaft seal 18 at an end near the working chamber 4, and the shaft seal 18 is used to prevent the liquid in the suction side liquid supply chamber 5 from flowing into the working chamber 4. The liquid discharged from the liquid return hole 7 of the liquid supply chamber at the suction end does not flow to the working chamber 4 any more, but flows into the inlet main pipeline 12 after being pressurized by the liquid pump. And the cryogenic liquid in the outlet main line 13 no longer flows to the working chamber 4.
Example 3
Since the low-temperature liquid injected into the exhaust-end bearing chamber 9 (via the exhaust-end liquid inlet hole 20) through the branch pipe 10 for supplying the low-temperature liquid in embodiment 1 mainly plays a role of lubricating the bearings in the exhaust-end bearing chamber 9, and it was found in practice that this low-temperature liquid cannot form a good liquid film heat transfer with the rotor shaft 19. The twin-screw compressor of this embodiment is provided with an annular groove for forming the discharge-side liquid supply chamber 21 (located in the casing of the compressor body 1) between the working chamber 4 and the discharge-side bearing chamber 9 of the compressor body 1, the annular groove being concentric with the rotor shaft 19 (the annular groove is provided on the inner wall of the chamber for communicating the working chamber 4 and the discharge-side bearing chamber 9 in the casing of the compressor body 1, and a minute gap is provided between the portion of the rotor shaft 19 near the discharge end face of the working chamber 4 and the chamber).
Referring to fig. 3, the casing of the compressor body 1 is provided with an exhaust end liquid inlet hole 20 and an exhaust end liquid supply chamber liquid return hole 22 which are communicated with an exhaust end liquid supply chamber 21. The exhaust-side liquid inlet 20 is connected to the branched pipe 10 for supplying the low-temperature liquid (i.e., unlike in embodiment 1, the branched pipe 10 for supplying the low-temperature liquid is not directly supplied with the low-temperature liquid to the exhaust-side bearing chamber 9 any more), and the liquid discharged from the suction-side liquid-supply-chamber liquid-return hole 7 and the exhaust-side liquid-supply-chamber liquid-return hole 22 flows to the working chamber 4.
Example 4
In order to be suitable for the dry oil-free occasion, the twin screw compressor of this embodiment is based on embodiment 3, in which the end of the discharge end liquid supply chamber 21 near the working chamber 4 is provided with a shaft seal 18, and in which the end of the suction end liquid supply chamber 5 near the working chamber 4 is also provided with a shaft seal 18. The liquid discharged from the suction side liquid supply chamber return hole 7 and the discharge side liquid supply chamber return hole 22 does not flow to the working chamber 4 any more, but flows into the inlet main pipe 12 after being pressurized by the liquid pump. And the cryogenic liquid in the outlet main line 13 no longer flows to the working chamber 4.
Claims (4)
1. The utility model provides a high rotor axial samming nature twin-screw compressor which characterized in that: the double-screw compressor comprises a compressor body (1) and a liquid supply system (2), wherein the compressor body (1) comprises a female rotor, a male rotor, a working cavity (4), a suction end bearing cavity (3) penetrated by one end of each of the male rotor and the female rotor, which extends out of the working cavity (4), and a discharge end bearing cavity (9) penetrated by the other end of each of the male rotor and the female rotor, which extends out of the working cavity (4), a suction end liquid supply chamber (5) is respectively arranged between the suction end bearing cavities (3) of the male rotor and the female rotor and the working cavity (4), the liquid supply system (2) comprises a cooler (11), an inlet main pipeline (12) for supplying high-temperature liquid, an outlet main pipeline (13) for supplying low-temperature liquid, and suction end branch pipelines for injecting the high-temperature liquid drained from the inlet main pipeline (12) and the low-temperature liquid drained from the outlet main pipeline (13) into each suction end liquid supply chamber (5), and the inlet main pipeline (12) and the outlet main pipeline (13) are respectively connected with the cooler (11);
the compressor body (1) further comprises annular grooves which are used for forming a suction end liquid supply chamber (5) respectively through matching with the male rotor and the female rotor;
the compressor body (1) further comprises an air suction end liquid inlet hole (6) for communicating the air suction end branch pipeline with each air suction end liquid supply chamber (5), and an air suction end liquid supply chamber liquid return hole (7) for leading out liquid from each air suction end liquid supply chamber (5); the aperture of the liquid return hole (7) of the liquid supply chamber at the air suction end is smaller than the aperture of the liquid inlet hole (6) at the air suction end;
an exhaust end liquid supply chamber (21) is respectively arranged between the exhaust end bearing chamber (9) and the working chamber (4) of the male rotor and the female rotor;
the compressor body (1) further comprises annular grooves for forming exhaust end liquid supply chambers (21) respectively through matching with the male rotor and the female rotor;
the liquid supply system (2) further comprises an exhaust end branch pipeline for injecting low-temperature liquid drained from the outlet main pipeline (13) into the exhaust end bearing cavity (9) or the exhaust end liquid supply chamber (21);
the compressor body (1) further comprises an exhaust end liquid inlet hole (20) for communicating the exhaust end branch pipeline with the exhaust end liquid supply chamber (21);
the compressor body (1) further comprises an exhaust end liquid supply chamber liquid return hole (22) for leading out liquid from the exhaust end liquid supply chamber (21).
2. The high rotor axial temperature uniformity twin screw compressor according to claim 1, wherein: the suction end liquid supply chamber (5) is communicated with the suction end bearing cavity (3) through a mounting gap of the rotor in the compressor body (1); the exhaust end liquid supply chamber (21) is communicated with the exhaust end bearing cavity (9) through an installation gap of the rotor in the compressor body (1).
3. The high rotor axial temperature uniformity twin screw compressor according to claim 1, wherein: an inlet bypass pipeline (14) is arranged on the inlet main pipeline (12), an outlet bypass pipeline (15) is arranged on the outlet main pipeline (13), and the inlet bypass pipeline (14) and the outlet bypass pipeline (15) are respectively connected with the branched pipeline at the air suction end; the inlet bypass pipeline (14) and the outlet bypass pipeline (15) are respectively provided with a flow regulating valve (17).
4. The high rotor axial temperature uniformity twin screw compressor according to claim 1, wherein: shaft seals (18) are arranged between the suction end liquid supply chamber (5) and the working cavity (4) and between the exhaust end liquid supply chamber (21) and the working cavity (4).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211274706.8A CN115507025B (en) | 2022-10-18 | 2022-10-18 | High rotor axial temperature uniformity twin-screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211274706.8A CN115507025B (en) | 2022-10-18 | 2022-10-18 | High rotor axial temperature uniformity twin-screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115507025A CN115507025A (en) | 2022-12-23 |
| CN115507025B true CN115507025B (en) | 2024-02-27 |
Family
ID=84511263
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211274706.8A Active CN115507025B (en) | 2022-10-18 | 2022-10-18 | High rotor axial temperature uniformity twin-screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115507025B (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2111662A (en) * | 1981-12-17 | 1983-07-06 | Sulzer Ag | Heat transfer apparatus comprising a refrigerant circuit |
| JPH08319976A (en) * | 1995-05-25 | 1996-12-03 | Hitachi Ltd | Oil-cooled type air compressor |
| JP2002039069A (en) * | 2000-07-21 | 2002-02-06 | Kobe Steel Ltd | Oil-cooled compressor |
| CN105927548A (en) * | 2016-06-21 | 2016-09-07 | 西安交通大学 | Water-spray screw steam compressor |
| CN105927547A (en) * | 2016-04-19 | 2016-09-07 | 西安交通大学 | Oil/water return structure of exhaust end sliding bearing of high-pressure helical-lobe compressor |
| CN106870329A (en) * | 2015-12-11 | 2017-06-20 | 阿特拉斯·科普柯空气动力股份有限公司 | Adjust the method for liquid injection, the compressor of liquid injection and the element of compressor |
| CN216554383U (en) * | 2021-11-04 | 2022-05-17 | 宁波鲍斯能源装备股份有限公司 | Screw rotor and double-screw air compressor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014041680A1 (en) * | 2012-09-14 | 2014-03-20 | 株式会社前川製作所 | Oil-cooled screw compressor system and oil-cooled screw compressor |
| BE1022403B1 (en) * | 2014-09-19 | 2016-03-24 | Atlas Copco Airpower Naamloze Vennootschap | METHOD FOR SENDING AN OIL-INJECTED COMPRESSOR DEVICE |
-
2022
- 2022-10-18 CN CN202211274706.8A patent/CN115507025B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2111662A (en) * | 1981-12-17 | 1983-07-06 | Sulzer Ag | Heat transfer apparatus comprising a refrigerant circuit |
| JPH08319976A (en) * | 1995-05-25 | 1996-12-03 | Hitachi Ltd | Oil-cooled type air compressor |
| JP2002039069A (en) * | 2000-07-21 | 2002-02-06 | Kobe Steel Ltd | Oil-cooled compressor |
| CN106870329A (en) * | 2015-12-11 | 2017-06-20 | 阿特拉斯·科普柯空气动力股份有限公司 | Adjust the method for liquid injection, the compressor of liquid injection and the element of compressor |
| CN105927547A (en) * | 2016-04-19 | 2016-09-07 | 西安交通大学 | Oil/water return structure of exhaust end sliding bearing of high-pressure helical-lobe compressor |
| CN105927548A (en) * | 2016-06-21 | 2016-09-07 | 西安交通大学 | Water-spray screw steam compressor |
| CN216554383U (en) * | 2021-11-04 | 2022-05-17 | 宁波鲍斯能源装备股份有限公司 | Screw rotor and double-screw air compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN115507025A (en) | 2022-12-23 |
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