CN109058109B - Compressor and air conditioner - Google Patents
Compressor and air conditioner Download PDFInfo
- Publication number
- CN109058109B CN109058109B CN201811178853.9A CN201811178853A CN109058109B CN 109058109 B CN109058109 B CN 109058109B CN 201811178853 A CN201811178853 A CN 201811178853A CN 109058109 B CN109058109 B CN 109058109B
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- CN
- China
- Prior art keywords
- compressor
- cylinders
- cylinder
- eccentric
- flange
- 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.)
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Links
- 238000006073 displacement reaction Methods 0.000 claims abstract description 22
- 230000000149 penetrating effect Effects 0.000 claims abstract description 3
- 238000005096 rolling process Methods 0.000 claims abstract description 3
- 238000005192 partition Methods 0.000 claims description 7
- 230000001502 supplementing effect Effects 0.000 abstract description 14
- 238000010438 heat treatment Methods 0.000 description 9
- 230000000694 effects Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
-
- 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
- F04C18/356—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 outer member
- F04C18/3562—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 outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a compressor and an air conditioner, wherein the compressor comprises: the device comprises two cylinders, rollers rolling in the cylinders, and crankshafts penetrating through the two cylinders, wherein two eccentric circles are arranged on the crankshafts at intervals, and each roller is internally provided with one eccentric circle. The total displacement of the two cylinders is in the range of 12.0cc to 16.5cc and the diameter of the eccentric circle is in the range of 20mm to 23.5 mm. The invention has the advantages of large opening area of the air supplementing port, sufficient air supplementing quantity, high energy efficiency of the compressor and the like.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a compressor and an air conditioner.
Background
In the low-temperature heating working condition of the existing compressor, when the refrigerant is lower than the evaporating temperature, the suction density is small, so that the heating quantity attenuation of the compressor at low temperature is serious, and the common method for solving the low-temperature attenuation of the compressor is an air supplementing technology. Fig. 1 shows a single-stage air supply structure of a conventional compressor, in which an air supply port 11 is disposed on an end cover of an air cylinder 1, and the air supply port 11 of a single-cylinder compressor is generally disposed on a lower flange, and the air supply principle is to realize opening and closing of the air supply port 11 by means of rotation of a roller 2. For a single-cylinder compressor with larger displacement, the diameter of the eccentric circle of the crankshaft is larger, so that the wall thickness of the roller 2 is thinner, the area on the end cover, where the air supplementing port 11 can be formed, is smaller, the air supplementing quantity can be reduced, and the leakage can be increased due to the fact that the diameter of the air supplementing port 11 is too large, so that the energy efficiency of the compressor is seriously affected.
Therefore, how to improve the energy efficiency of the existing compressor is a technical problem to be solved in the industry.
Disclosure of Invention
In order to solve the defect of low energy efficiency of a compressor in the prior art, the invention provides the compressor and an air conditioner.
The technical scheme adopted by the invention is that the compressor is designed, and comprises: the device comprises two cylinders, rollers rolling in the cylinders, and crankshafts penetrating through the two cylinders, wherein two eccentric circles are arranged on the crankshafts at intervals, and each roller is internally provided with one eccentric circle. The total displacement of the two cylinders is in the range of 12.0cc to 16.5cc, and the diameter of each eccentric circle is in the range of 20mm to 23.5 mm.
The two eccentric circles are respectively a first eccentric circle close to the first flange and a second eccentric circle close to the second flange. A partition plate is arranged between the two cylinders, an air supplementing hole communicated with the two cylinders is formed in the partition plate, the two cylinders are arranged in the shell, and the air supplementing hole is connected with an air supplementing pipe extending out of the shell through a connecting pipe.
Preferably, the two cylinders are a first cylinder and a second cylinder respectively, and the inner radius of the first cylinder is R 1 The outer circle radius of the roller in the first cylinder is r 1 The cylinder height of the first cylinder is h 1 The inner circle radius of the second cylinder is R 2 The outer circle radius of the roller in the second cylinder is r 2 The cylinder height of the second cylinder is h 2 Total displacement v=pi×h 1 ×(R 1 2 －r 1 2 )+π×h 2 ×(R 2 2 －r 2 2 )。
Preferably, the diameter of the shaft section of the crankshaft, which is positioned in the first flange, is B, and B is more than or equal to 10mm and less than or equal to 16.6mm.
Preselected, the diameter of the first eccentric circle is A 1 The eccentric amount is e 1 ，
Preferably, the diameter of the shaft section of the crankshaft, which is positioned in the second flange, is C, and C is more than or equal to 10mm and less than or equal to 16.6mm.
Preferably, the diameter of the second eccentric circle is A 2 The eccentric amount is e 2 ，
Preferably, the eccentric amount of each eccentric circle is in the range of 3.4mm to 3.8 mm.
Preferably, the cylinder height of each cylinder is in the range of 14mm to 16 mm.
Preferably, both cylinders are identical in shape and displacement.
Preferably, the two eccentric circles are identical in shape.
The invention also provides an air conditioner comprising the compressor.
Compared with the prior art, the double-cylinder compressor is adopted, the displacement and the eccentric circle diameter of the compressor are limited, so that the area of the separator of the compressor, which can be provided with the air supply port, is increased, the sufficient air supply quantity of the compressor is ensured, leakage is effectively reduced, and the energy efficiency of the compressor is greatly improved.
Drawings
The invention is described in detail below with reference to examples and figures, wherein:
FIG. 1 is a schematic illustration of a prior art single stage air make-up configuration for a compressor;
FIG. 2 is a schematic diagram of the air make-up structure of the compressor in the preferred embodiment of the present invention;
FIG. 3 is a schematic view of a crankshaft in a preferred embodiment of the present invention;
FIG. 4 is a schematic view showing a connection structure of a cylinder and a crankshaft in a preferred embodiment of the present invention;
FIG. 5 is a schematic view of the structure of section A-A of FIG. 4;
FIG. 6 is a graph of compressor displacement versus performance for a first heating operation;
FIG. 7 is a graph of compressor displacement versus performance for a second heating operation;
fig. 8 is a graph of eccentric circle diameter versus compressor performance.
Detailed Description
As shown in fig. 2 and 3, the compressor according to the present invention includes: the device comprises two cylinders 1, two rollers 2, a crankshaft 3 and other components, wherein one roller 2 is arranged in each cylinder 1, the rollers 2 roll along the inner circular surface of the cylinder 1, the crankshaft 3 passes through the two cylinders 1, the crankshaft 3 is provided with two eccentric circles 31 which are arranged at intervals along the axial direction of the crankshaft, and one eccentric circle 31 is correspondingly arranged in each roller 3. The two cylinders 1 are separated by a partition plate 4, the partition plate 4 is provided with an air supplementing hole 41 communicated with the two cylinders 1, and the position, close to the cylinders, of the air supplementing hole 41 is an air supplementing port 11. Two cylinders 1 are installed in casing 5, and the air make-up hole 41 passes through connecting pipe 6 and connects the air make-up pipe 7 that stretches out outside casing 5, and air make-up hole 41 and connecting pipe 6 tight fit seal, and air make-up hole 41, connecting pipe 6 and air make-up pipe 7 have constituted the air make-up passageway jointly.
According to the invention, the double-cylinder compressor is adopted, and for a single-cylinder compressor with the same displacement, the displacement of the double-cylinder compressor is shared by two cylinders 1, so that the eccentric amount of an eccentric circle 31 in a single cylinder 1 is effectively reduced, the wall thickness of a roller 2 is increased, and the opening area of a gas supplementing port 11 is larger.
As shown in fig. 4 and 5, the two cylinders 1 are a first cylinder and a second cylinder, respectively, and the inner radius of the first cylinder is R 1 The outer circle radius of the roller in the first cylinder is r 1 The cylinder height of the first cylinder is h 1 The inner circle radius of the second cylinder is R 2 The outer circle radius of the roller in the second cylinder is r 2 The cylinder height of the second cylinder is h 2 Total displacement v=pi×h 1 ×(R 1 2 －r 1 2 )+π×h 2 ×(R 2 2 －r 2 2 ) In the preferred embodiment, both cylinders 1 are identical in shape and displacement, with a total displacement V of twice the displacement of a single cylinder. Table 1 below shows the relationship between compressor displacement and performance for the first heating regime, where an increase in compressor power results in a significant decrease in energy efficiency ratio at nominal heating regime (-12 ℃) when compressor displacement V is 16.5cc or greater, the variation of which is seen in the graph of FIG. 6; table 2 below shows that at nominal heating conditions (-20 ℃) the compressor power rise significantly results in a significant decrease in the energy efficiency ratio when the compressor displacement V is less than or equal to 12.0cc under the second heating conditions, the variation of which is seen in the graph shown in FIG. 7. Therefore, the displacement of the compressor is most preferably in the range of 12.0 cc.ltoreq.V.ltoreq.16.5.
Table 1:
table 2:
the diameter of the eccentric circle 31 is designed on the basis of the determined displacement of the compressor, and the purpose is to reduce the diameter of the eccentric circle 31 so as to increase the diameter of the inner circle of the roller 2, so that the area of the partition plate 4 provided with the air compensating port 11 is increased, the air compensating amount is increased, the sealing distance is increased so as to reduce leakage, and the effect of improving the energy efficiency is achieved. Table 3 below shows the relationship between the eccentric circle 31 and the performance of the compressor, when the diameter of the eccentric circle 31 is greater than 23.5mm, the area where the air supply port 11 can be opened is too small, the diameter of the opened air supply port 11 is reduced, the air supply effect of the compressor is poor, the heating amount is low under the low-temperature working condition, and finally the energy efficiency ratio of the compressor is very low; when the diameter of the deflection circle 31 is smaller than 20mm, shafting instability of the compressor starts to occur, resulting in high compressor power, and eventually very low energy efficiency, even unstable operation, and the variation thereof is shown in the graph of fig. 8. Therefore, the diameters of the two eccentric circles 31 are limited to be in the range of 20mm to 23.5mm, so that the running stability of the compressor is ensured, the compressor has good air supplementing effect and high energy efficiency, and in the preferred embodiment, the two eccentric circles 31 are identical in shape.
Table 3:
as shown in fig. 2 to 4, a first flange 8 is sleeved at one end of the crankshaft 3, a second flange 9 is sleeved at the other end of the crankshaft 3, two cylinders 1 are clamped between the first flange 8 and the second flange 9, the diameter of a shaft section of the crankshaft 3, which is positioned in the first flange 8, is B, which is more than or equal to 10mm, is less than or equal to 16.6mm, the diameter of a shaft section of the crankshaft 3, which is positioned in the second flange 9, is C, which is more than or equal to 10mm, is less than or equal to 16.6mm, so that the crankshaft 3 has better structural strength and the energy efficiency of a compressor can be improved. Preferably, the eccentric amounts of the two eccentric circles 31 are limited to be within the range of 3.4mm to 3.8mm, so that the energy efficiency of the compressor can be effectively improved. Further, the cylinder heights of the two cylinders 1 are limited to be in the range of 14mm to 16mm, so that the energy efficiency of the compressor can be effectively improved.
Still further, as shown in fig. 3 and 4, the two eccentric circles 31 are a first eccentric circle near the first flange 8 and a second eccentric circle near the second flange 9, respectively, the diameter of the first eccentric circle is a 1 The eccentric amount is e 1 ，The diameter of the second eccentric circle is A 2 The eccentric amount is e 2 ，/>This condition is satisfied in order to ensure that the rollers 2 can be smoothly fit on the first eccentric circle and the second eccentric circle, respectively.
The invention also provides an air conditioner comprising the compressor.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention.
Claims (14)
1. A compressor, comprising: the device comprises two cylinders, rollers rolling in the cylinders, and crankshafts penetrating through the two cylinders, wherein two eccentric circles are arranged on the crankshafts at intervals, and each roller is internally provided with one eccentric circle correspondingly; wherein the total displacement of the two cylinders is in the range of 12.0cc to 16.5cc, and the diameter of each eccentric circle is in the range of 20mm to 23.5 mm.
2. The compressor of claim 1, wherein the two cylinders are a first cylinder and a second cylinder, respectively, and the first cylinder has an inner radius R 1 The outer circle radius of the roller in the first cylinder is r 1 The cylinder height of the first cylinder is h 1 The inner circle radius of the second cylinder is R 2 The outer circle radius of the roller in the second cylinder is r 2 The cylinder height of the second cylinder is h 2 Total displacement v=pi×h 1 ×(R 1 ²－r 1 ²)+π×h 2 ×(R 2 ²－r 2 ²)。
3. The compressor of claim 1, wherein a first flange is sleeved on one end of the crankshaft, a second flange is sleeved on the other end of the crankshaft, the two cylinders are clamped between the first flange and the second flange, and the two eccentric circles are a first eccentric circle near the first flange and a second eccentric circle near the second flange, respectively.
4. A compressor according to claim 3, wherein the diameter of the shaft section of the crankshaft located in the first flange is B,10 mm.ltoreq.b.ltoreq.16.6 mm.
5. The compressor of claim 4, wherein the first eccentric circle has a diameter A 1 The eccentric amount is e 1 ，≥e 1 。
6. A compressor according to claim 3, wherein the diameter of the shaft section of the crankshaft located in the second flange is C,10mm C16.6 mm or less.
7. The compressor of claim 6, wherein the diameter of the second eccentric circle is a 2 The eccentric amount is e 2 ，≥e 2 。
8. The compressor of claim 1, wherein an eccentric amount of each of the eccentric circles is in a range of 3.4mm to 3.8 mm.
9. The compressor of claim 1, wherein a cylinder height of each of the cylinders is in a range of 14mm to 16 mm.
10. A compressor according to any one of claims 1 to 9, wherein a partition plate is provided between the two cylinders, and an air supply hole communicating the two cylinders is provided in the partition plate.
11. The compressor of claim 10, wherein the two cylinders are installed in a housing, and the air supply hole is connected to an air supply pipe extending outside the housing through a connection pipe.
12. A compressor as claimed in any one of claims 1 to 9 wherein the shape and displacement of both cylinders are the same.
13. A compressor according to any one of claims 1 to 9, wherein the two eccentric circles are identical in shape.
14. An air conditioner, comprising: a compressor as claimed in any one of claims 1 to 13.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811178853.9A CN109058109B (en) | 2018-10-10 | 2018-10-10 | Compressor and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811178853.9A CN109058109B (en) | 2018-10-10 | 2018-10-10 | Compressor and air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109058109A CN109058109A (en) | 2018-12-21 |
| CN109058109B true CN109058109B (en) | 2024-02-27 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811178853.9A Active CN109058109B (en) | 2018-10-10 | 2018-10-10 | Compressor and air conditioner |
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| Country | Link |
|---|---|
| CN (1) | CN109058109B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112145421A (en) * | 2019-06-27 | 2020-12-29 | 上海海立电器有限公司 | Compressor, air conditioner outdoor unit, air conditioning system and assembling method of compression unit |
| CN112576514B (en) * | 2020-11-30 | 2022-09-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body assembly, compressor and air conditioner with same |
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| CN1779262A (en) * | 2004-11-26 | 2006-05-31 | 日立家用电器公司 | Double-cylinder rotary compressor and air conditioner therewith |
| JP2006200373A (en) * | 2005-01-18 | 2006-08-03 | Sanyo Electric Co Ltd | Rotary compressor |
| CN101012831A (en) * | 2007-01-29 | 2007-08-08 | 西安庆安制冷设备股份有限公司 | Rotor type twin cylinder compressor taking air-breathing through partition board |
| KR20090012866A (en) * | 2007-07-31 | 2009-02-04 | 엘지전자 주식회사 | Rotary compressor |
| CN106122019A (en) * | 2016-08-09 | 2016-11-16 | 珠海凌达压缩机有限公司 | Rotary compressor |
| JP2018044489A (en) * | 2016-09-14 | 2018-03-22 | 東芝キヤリア株式会社 | Rotation type compressor and refrigeration cycle device |
| CN207131581U (en) * | 2017-05-26 | 2018-03-23 | 广东美芝精密制造有限公司 | The compression mechanism and twin-tub rotation-type compressor of twin-tub rotation-type compressor |
| CN207195203U (en) * | 2017-09-04 | 2018-04-06 | 珠海凌达压缩机有限公司 | Air supplement structure of compressor and compressor with air supplement structure |
| CN208982282U (en) * | 2018-10-10 | 2019-06-14 | 珠海凌达压缩机有限公司 | Compressor and air conditioner |
-
2018
- 2018-10-10 CN CN201811178853.9A patent/CN109058109B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1779262A (en) * | 2004-11-26 | 2006-05-31 | 日立家用电器公司 | Double-cylinder rotary compressor and air conditioner therewith |
| JP2006200373A (en) * | 2005-01-18 | 2006-08-03 | Sanyo Electric Co Ltd | Rotary compressor |
| CN101012831A (en) * | 2007-01-29 | 2007-08-08 | 西安庆安制冷设备股份有限公司 | Rotor type twin cylinder compressor taking air-breathing through partition board |
| KR20090012866A (en) * | 2007-07-31 | 2009-02-04 | 엘지전자 주식회사 | Rotary compressor |
| CN106122019A (en) * | 2016-08-09 | 2016-11-16 | 珠海凌达压缩机有限公司 | Rotary compressor |
| JP2018044489A (en) * | 2016-09-14 | 2018-03-22 | 東芝キヤリア株式会社 | Rotation type compressor and refrigeration cycle device |
| CN207131581U (en) * | 2017-05-26 | 2018-03-23 | 广东美芝精密制造有限公司 | The compression mechanism and twin-tub rotation-type compressor of twin-tub rotation-type compressor |
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| CN208982282U (en) * | 2018-10-10 | 2019-06-14 | 珠海凌达压缩机有限公司 | Compressor and air conditioner |
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| Publication number | Publication date |
|---|---|
| CN109058109A (en) | 2018-12-21 |
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