CN114087181B - Pump body assembly, two-stage compressor and air conditioning system - Google Patents
Pump body assembly, two-stage compressor and air conditioning system Download PDFInfo
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- CN114087181B CN114087181B CN202111500729.1A CN202111500729A CN114087181B CN 114087181 B CN114087181 B CN 114087181B CN 202111500729 A CN202111500729 A CN 202111500729A CN 114087181 B CN114087181 B CN 114087181B
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- cylinder
- eccentric part
- sliding vane
- vane groove
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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
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
Abstract
The application provides a pump body assembly, a two-stage compressor and an air conditioning system. The pump body assembly comprises a crankshaft, a first eccentric part and a second eccentric part; the first cylinder is sleeved on the first eccentric part and is provided with a first sliding vane groove; the second cylinder is sleeved on the second eccentric part and is provided with a second sliding vane groove; the included angle between the first eccentric part and the second eccentric part is 180 degrees, the included angle between the central lines of the first sliding vane groove and the second sliding vane groove is alpha, and the included angle is more than or equal to 60 degrees and less than 120 degrees. According to the method, the relative position angle of the first cylinder and the second cylinder is reasonably designed, so that the connection smoothness of the exhaust of the first cylinder and the suction of the second cylinder is improved, the pressure pulsation of the middle cavity and the suction and vacuumizing condition of the high-pressure stage are reduced, and the performance is improved.
Description
Technical Field
The application belongs to the technical field of two-stage compressors, and particularly relates to a pump body assembly, a two-stage compressor and an air conditioning system.
Background
The pump body of the existing two-stage compressor comprises two sets of compression assemblies (the compression assemblies comprise parts such as a cylinder, a sliding vane, a roller, a crankshaft and the like, two closed working cavities are formed by the inner circle of the cylinder, the outer circle of the roller and the head of the sliding vane, one cavity is an air suction cavity, the other cavity is a compression cavity), the low-pressure stage compression assembly compresses refrigerant from low-temperature low-pressure vapor to medium-temperature medium-pressure vapor, then the refrigerant is discharged to the middle cavity and mixed with gas from a flash evaporator in an air conditioning system, the high-pressure stage compression assembly absorbs the medium-temperature medium-pressure vapor from the middle cavity, and then the compressed high-temperature high-pressure gas is discharged to the cavity of the shell of the compressor.
The working chamber (including the suction chamber and the compression chamber) is a crescent chamber as shown in fig. 1, so that the volume change rates of the suction/compression chambers of the low pressure stage and the high pressure stage are different in one cycle of 360 ° rotation of the compression assembly (the volume change rate refers to the change value of the suction chamber/compression chamber volume every 1 ° rotation of the crankshaft/roller), and thus there is a problem as follows: when the low-pressure stage compression assembly reaches the maximum exhaust rate, the high-pressure stage compression assembly generates pressure pulsation in the middle cavity at the moment when the suction rate is not the maximum, so that pulsation loss is caused; in another state, when the high-pressure stage suction rate is maximum and the low-pressure stage discharge rate is smaller, the high-pressure stage suction is insufficient, a vacuum pumping phenomenon is generated, power consumption is increased, and the performance of the compressor is not good.
Disclosure of Invention
Therefore, the application provides a pump body assembly, a two-stage compressor and an air conditioning system, which can solve the problem that the low-pressure stage compression assembly and the high-pressure stage compression assembly in the prior art are not matched in operation.
In order to solve the above-mentioned problem, this application provides a pump body subassembly, includes:
a crankshaft including a first eccentric portion and a second eccentric portion;
the first cylinder is sleeved on the first eccentric part and is provided with a first sliding vane groove;
the second cylinder is sleeved on the second eccentric part and is provided with a second sliding vane groove;
the included angle between the first eccentric part and the second eccentric part is 180 degrees, the included angle between the central lines of the first sliding vane groove and the second sliding vane groove is alpha, and the included angle is more than or equal to 60 degrees and less than 120 degrees.
Optionally, the included angle of the central lines of the first sliding vane groove and the second sliding vane groove is alpha, and the included angle is more than or equal to 80 degrees and less than 110 degrees.
A pump body assembly, comprising:
a crankshaft including a first eccentric portion and a second eccentric portion;
the first cylinder is sleeved on the first eccentric part and is provided with a first sliding vane groove;
the second cylinder is sleeved on the second eccentric part and is provided with a second sliding vane groove;
the included angle between the first sliding vane groove and the second sliding vane groove is 0 degrees, the included angle between the first eccentric part and the second eccentric part is beta, and the included angle is more than or equal to 80 degrees and less than or equal to 140 degrees.
Optionally, the included angle between the first eccentric part and the second eccentric part is beta, and beta is more than or equal to 80 degrees and less than or equal to 110 degrees.
According to another aspect of the present application, there is provided a dual stage compressor comprising a pump body assembly as described above.
Optionally, the dual-stage compressor comprises a partition plate, and the partition plate is arranged between the first cylinder and the second cylinder; and an air flow channel is arranged on the partition plate, and an exhaust port of the first cylinder is conveyed to the second cylinder through the air flow channel.
Optionally, the partition board comprises a first partition board and a second partition board, the first partition board and the second partition board are in abutting connection, and a medium pressure cavity is formed between the first partition board and the second partition board; the air flow channel penetrates through the medium-pressure cavity.
According to yet another aspect of the present application, there is provided an air conditioning system comprising a pump body assembly as described above or a dual stage compressor as described above.
Optionally, the air conditioning system further comprises a flash evaporator, wherein the flash evaporator is communicated with the air flow channel and can supplement air and increase enthalpy into the air flow channel.
The application provides a pump body subassembly, include: a crankshaft including a first eccentric portion and a second eccentric portion; the first cylinder is sleeved on the first eccentric part and is provided with a first sliding vane groove; the second cylinder is sleeved on the second eccentric part and is provided with a second sliding vane groove; the included angle between the first eccentric part and the second eccentric part is 180 degrees, the included angle between the central lines of the first sliding vane groove and the second sliding vane groove is alpha, and the included angle is more than or equal to 60 degrees and less than 120 degrees.
According to the method, the relative position angle of the first cylinder and the second cylinder is reasonably designed, so that the connection smoothness of the exhaust of the first cylinder and the suction of the second cylinder is improved, the pressure pulsation of the middle cavity and the suction and vacuumizing condition of the high-pressure stage are reduced, and the performance is improved.
Drawings
FIG. 1 is a schematic diagram of the principle of operation of a two-stage compressor;
FIG. 2 is an axial cross-sectional structural schematic view of a pump body assembly of an embodiment of the present application;
FIG. 3 is a schematic transverse cross-sectional view of a pump body assembly of an embodiment of the present application;
FIG. 4 is another schematic transverse cross-sectional view of a pump body assembly of an embodiment of the present application;
fig. 5 is a schematic diagram of performance enhancement amplitude of a dual stage compressor according to an embodiment of the present application.
The reference numerals are expressed as:
1. a first cylinder; 11. a first slider groove; 2. a second cylinder; 21. a second slide groove; 3. a partition plate; 4. a crankshaft; 41. a first eccentric portion; 42. a second eccentric portion.
Detailed Description
Referring now to fig. 1-5 in combination, in accordance with an embodiment of the present application, a pump body assembly includes:
a crankshaft 4 including a first eccentric portion 41 and a second eccentric portion 42;
the first cylinder 1 is sleeved on the first eccentric part 41, and a first sliding vane groove 11 is formed in the first cylinder 1;
the second cylinder 2 is sleeved on the second eccentric part 42, and a second sliding vane groove 21 is formed in the second cylinder 2;
the included angle between the first eccentric part 41 and the second eccentric part 42 is 180 degrees, the included angle between the central lines of the first sliding vane groove 11 and the second sliding vane groove 21 is alpha, and the included angle is 60 degrees less than or equal to alpha less than 120 degrees.
Preferably, the included angle between the central lines of the first slide groove 11 and the second slide groove 21 is alpha, and the included angle is 80 degrees less than or equal to alpha and less than 110 degrees.
The first cylinder 1 and the second cylinder 2 form a multi-stage pump body assembly, the first sliding vane groove 11 in the first cylinder 1 in the low-pressure stage compression assembly is taken as a reference, the included angle alpha between the second sliding vane groove 21 in the second cylinder 2 of the high-pressure stage compression assembly and the second sliding vane groove is 60 degrees to 120 degrees in a top view of the pump body assembly, the second sliding vane groove 21 is arranged in the anticlockwise direction of the first sliding vane groove 11, at the moment, when the exhaust rate of the first cylinder 1 reaches the maximum, the air suction rate of the second cylinder 2 is in a larger state, so that the exhaust of the first cylinder 1 stays in the middle cavity, the pressure pulsation loss is generated, and the performance of the compressor is effectively improved. Meanwhile, in this state, when the suction rate of the second cylinder 2 is large, the exhaust rate of the first cylinder 1 is at a large level, avoiding the occurrence of a serious vacuum phenomenon, resulting in an increase in power consumption.
Further, five different vane slot angles are designed for new performance evaluation criteria of the compressor, and the performance is tested by prototype, and it is found that when the included angle α between the second vane slot 21 of the second cylinder 2 and the second vane slot 21 of the first cylinder 1 is 80 ° -110 °, as shown in fig. 5, the performance of the compressor is improved greatly, and the improvement on high frequency is more remarkable.
A pump body assembly, comprising:
a crankshaft 4 including a first eccentric portion 41 and a second eccentric portion 42;
the first cylinder 1 is sleeved on the first eccentric part 41, and a first sliding vane groove 11 is formed in the first cylinder 1;
the second cylinder 2 is sleeved on the second eccentric part 42, and a second sliding vane groove 21 is formed in the second cylinder 2;
the included angle between the first sliding vane groove 11 and the second sliding vane groove 21 is 0 degrees, the included angle between the first eccentric part 41 and the second eccentric part 42 is beta, and the included angle is more than or equal to 80 degrees and less than or equal to 140 degrees.
Preferably, the angle between the first eccentric portion 41 and the second eccentric portion 42 is beta, satisfying 80 degrees.ltoreq.beta.ltoreq.110 degrees.
Different from the above-mentioned angle difference limiting two sliding vane grooves, the sliding vane groove angle in the two cylinders is 0 DEG, and when the included angle beta between the first eccentric part 41 and the second eccentric part 42 on the crankshaft 4 is 80 DEG to 140 DEG, the suction rate of the second cylinder 2 can be ensured to be in a larger state when the discharge rate of the first cylinder 1 is larger, and meanwhile, the redundant power consumption caused by the vacuum suction of the suction cavity of the high-pressure compression assembly can be improved to a certain extent, and the performance of the compressor can be effectively improved.
According to another aspect of the present application, there is provided a dual stage compressor comprising a pump body assembly as described above.
In some embodiments, the dual-stage compressor comprises a partition 3, said partition 3 being arranged between said first cylinder 1 and said second cylinder 2; the partition plate 3 is provided with an air flow channel, and the exhaust port of the first cylinder 1 is conveyed to the second cylinder 2 through the air flow channel.
Preferably, the partition board 3 comprises a first partition board and a second partition board, the first partition board and the second partition board are in abutting connection, and a medium pressure cavity is formed between the first partition board and the second partition board; the air flow channel penetrates through the medium-pressure cavity.
In the prior art, the first cylinder 1 generally adopts a double-row structure, and particularly, exhaust ports are formed in the lower flange and the lower partition plate 3, a part of exhaust gas after primary compression is directly discharged to the middle cavity of the middle partition plate 3 through the exhaust ports on the lower partition plate 3 and then is inhaled by the upper cylinder, and the other part of exhaust gas is discharged to the middle cavity of the lower flange through the exhaust ports on the lower flange, then enters the middle cavity of the lower partition plate 3 through the lower flange, the lower cylinder and the middle circulating channel on the lower partition plate 3 and is inhaled by the upper cylinder, so that the circulating channel of the lower exhaust gas is longer, the circulating loss of the lower exhaust gas is increased, and especially the influence of high-frequency working conditions is more serious.
Therefore, the low-pressure-stage exhaust to high-pressure-stage air suction circulation channel of the existing two-stage compressor is longer, and the flow loss is larger, the first cylinder 1 is designed to be of a single exhaust structure, and the low-pressure-stage exhaust cavity is arranged in the middle pressure cavity of the partition plate 3 of the connecting section of the eccentric part of the high-pressure-stage and the low-pressure-stage, so that the exhaust of one stage is directly sucked by the air suction cavity of the high-pressure-stage compression assembly after being discharged, the flow loss of the exhaust of the low-pressure-stage is effectively reduced, and the performance of the compressor is improved.
According to yet another aspect of the present application, there is provided an air conditioning system comprising a pump body assembly as described above or a dual stage compressor as described above.
In some embodiments, the air conditioning system further comprises a flash evaporator, wherein the flash evaporator is communicated with the air flow channel and can supplement air and increase enthalpy into the air flow channel.
In the air conditioning circulation system, the gas in the flash evaporator is injected into the airflow channel to play a role in supplementing gas and increasing enthalpy, and the performance of the air conditioning system with the two-stage compressor is improved.
It is easy to understand by those skilled in the art that the above embodiments can be freely combined and overlapped without conflict.
The foregoing description of the preferred embodiments of the present application is not intended to be limiting, but is intended to cover any and all modifications, equivalents, and alternatives falling within the spirit and principles of the present application. The foregoing is merely a preferred embodiment of the present application, and it should be noted that, for a person skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present application, and these improvements and modifications should also be considered as the protection scope of the present application.
Claims (7)
1. A pump body assembly, comprising:
a crankshaft (4) including a first eccentric portion (41) and a second eccentric portion (42);
the first air cylinder (1) is sleeved on the first eccentric part (41), and a first sliding vane groove (11) is formed in the first air cylinder (1);
the second cylinder (2) is sleeved on the second eccentric part (42), and a second sliding vane groove (21) is formed in the second cylinder (2);
the included angle between the first eccentric part (41) and the second eccentric part (42) is 180 degrees, the included angle between the central lines of the first sliding vane groove (11) and the second sliding vane groove (21) is alpha, and the included angle is more than or equal to 80 degrees and less than 110 degrees.
2. A pump body assembly, comprising:
a crankshaft (4) including a first eccentric portion (41) and a second eccentric portion (42);
the first air cylinder (1) is sleeved on the first eccentric part (41), and a first sliding vane groove (11) is formed in the first air cylinder (1);
the second cylinder (2) is sleeved on the second eccentric part (42), and a second sliding vane groove (21) is formed in the second cylinder (2);
the included angle between the first sliding vane groove (11) and the second sliding vane groove (21) is 0 degrees, the included angle between the first eccentric part (41) and the second eccentric part (42) is beta, and the included angle is more than or equal to 80 degrees and less than or equal to 110 degrees.
3. A two-stage compressor comprising a pump body assembly according to any one of claims 1-2.
4. -the two-stage compressor according to claim 3, characterized in that it comprises a partition (3), said partition (3) being arranged between said first cylinder (1) and said second cylinder (2); an air flow channel is arranged on the partition plate (3), and an exhaust port of the first air cylinder (1) is conveyed to the second air cylinder (2) through the air flow channel.
5. The two-stage compressor according to claim 4, characterized in that the partition (3) comprises a first partition and a second partition, which are arranged in abutment and between which a medium-pressure chamber is formed; the air flow channel penetrates through the medium-pressure cavity.
6. An air conditioning system comprising a pump body assembly according to any one of claims 1-2 or a dual stage compressor according to any one of claims 3-5.
7. An air conditioning system according to claim 6, characterized in that a partition plate (3) is arranged between the first air cylinder (1) and the second air cylinder (2), and an air flow channel which communicates the first air cylinder (1) and the second air cylinder (2) is arranged on the partition plate (3); the air conditioning system further comprises a flash evaporator, wherein the flash evaporator is communicated with the air flow channel and can supplement air and increase enthalpy into the air flow channel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111500729.1A CN114087181B (en) | 2021-12-09 | 2021-12-09 | Pump body assembly, two-stage compressor and air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111500729.1A CN114087181B (en) | 2021-12-09 | 2021-12-09 | Pump body assembly, two-stage compressor and air conditioning system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114087181A CN114087181A (en) | 2022-02-25 |
| CN114087181B true CN114087181B (en) | 2023-05-23 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202111500729.1A Active CN114087181B (en) | 2021-12-09 | 2021-12-09 | Pump body assembly, two-stage compressor and air conditioning system |
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Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3490950B2 (en) * | 2000-03-15 | 2004-01-26 | 三洋電機株式会社 | 2-cylinder 2-stage compression type rotary compressor |
| JP5199863B2 (en) * | 2008-12-26 | 2013-05-15 | 三洋電機株式会社 | Rotary compressor |
| CN202250863U (en) * | 2011-06-30 | 2012-05-30 | 珠海格力电器股份有限公司 | Double-stage rotating compressor |
| WO2015081543A1 (en) * | 2013-12-05 | 2015-06-11 | 广东美芝制冷设备有限公司 | Rotary compressor and compression unit thereof, and air conditioner |
| CN104632623B (en) * | 2013-12-23 | 2017-02-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Double-stage compressor |
| CN104632624B (en) * | 2013-12-25 | 2016-10-05 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of twin-tub double-stage compressor |
| CN104632627A (en) * | 2014-07-28 | 2015-05-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor pump body and compressor comprising same |
| CN104564675A (en) * | 2014-11-04 | 2015-04-29 | 广东美芝制冷设备有限公司 | Dual-cylinder rotation type compressor and refrigerator with same |
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2021
- 2021-12-09 CN CN202111500729.1A patent/CN114087181B/en active Active
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| CN114087181A (en) | 2022-02-25 |
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