CN105041651A - Compressor and air-conditioning system with same - Google Patents
Compressor and air-conditioning system with same Download PDFInfo
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- CN105041651A CN105041651A CN201510402156.7A CN201510402156A CN105041651A CN 105041651 A CN105041651 A CN 105041651A CN 201510402156 A CN201510402156 A CN 201510402156A CN 105041651 A CN105041651 A CN 105041651A
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Abstract
The invention discloses a compressor and an air-conditioning system with the same. The compressor comprises a shell, a cylinder assembly and a motor assembly. The shell is provided with an exhaust outlet. The cylinder assembly is arranged in the shell, and is provided with a compression cavity. The motor assembly is arranged in the shell, a first fluid channel which is communicated with the compression cavity and the exhaust outlet is formed in the motor assembly, and a second fluid channel is formed between the motor assembly and the shell in a limited mode. Refrigerant is propane, the minimum cross sectional area of the first fluid channel and the minimum cross sectional area of the second fluid channel in the flowing direction of the refrigerant are G1 and G2 respectively, and the delivery volume of the compressor is D. The G1, the G2 and the D meet the following relational expressions that f=D*<rho>d/G1 and h=D*<rho>d/G2, wherein f is larger than or equal to 0.1 g/cm<2> and is smaller than or equal to 2.1 g/cm<2>, h is larger than or equal to 0.06 g/cm<2> and is smaller than or equal to 0.7 g/cm<2>, and <rho>d is equal to 0.038 g/cm<3>. According to the compressor, exhausting and oil returning are smoother, power consumption is low, and operating efficiency is improved.
Description
Technical field
The present invention relates to air-conditioning technical field, more specifically, relate to a kind of compressor and there is its air-conditioning system.
Background technique
R22 refrigeration agent is classified as by " Montreal is discussed and decided " book the refrigeration agent that time limit progressively eliminates.Europe, Japan start to turn to R410A refrigerant replacement already, and the U.S. also starts to forbid the use of R22 in new refrigeration product.China also accelerates the paces that R22 eliminates, and within 2015, will reach the requirement of 10% of reduction baseline values.And more domestic major brand also start to release the environment-friendly air conditioner of R410A as refrigeration agent.But the GWP value of R410A is also larger than R22, R410A has been classified as the greenhouse gases of controlled discharge by " Kyoto Protocol ", and all R410A are never long-range replacement schemes.
The R290 of one of refrigeration agent, i.e. propane as an alternative, for industry is paid close attention to.But when the refrigeration agent used in air-conditioning changes, the structure of air-conditioning also should adjust.
Summary of the invention
The application makes the discovery of the following fact and problem and understanding based on inventor:
Inventor tests using the air-conditioning system of R290 refrigeration agent, find under air-conditioning ASHRAE test condition, no matter compressor is in suction condition or exhaust condition, adopt R290 refrigeration agent more much lower than the mass flow rate of R22 refrigeration agent, be about 45% ~ 48% of R22 refrigeration agent, specifically as shown in table 1.
Table 1
As for latent heat of vaporization aspect, at 40 DEG C and 10 DEG C, R290 refrigeration agent is 3-4 times of R22 refrigeration agent.Specifically as shown in table 2.Because the latent heat of vaporization is higher, unit mass refrigerant suction or liberated heat more.Therefore, actual air-conditioning, when mating, obtain identical refrigerating capacity, when adopting R290 refrigeration agent, only needs the filling quantity (quality) of 25% ~ 40% of R22 refrigeration agent in the past.Like this, in compressor and air-conditioning system, R290 refrigeration agent is more much lower than the mass flow rate of R22 refrigeration agent.
Table 2
Certainly, because the refrigerating effect per unit swept volume of R290 refrigeration agent is about 85% of R22 refrigeration agent.Therefore, identical refrigerating capacity be obtained, adopt the discharge volume ratio of the compressor with rolling rotor of R290 refrigeration agent to adopt during R22 refrigeration agent and want greatly a bit.
In view of this, present inventor is specially for adopting the air-conditioning system of R290 refrigeration agent to be studied, wherein improve the structure of compressor especially, make the compressor after improvement and air-conditioning system thereof can mate R290 refrigeration agent, usability is better.
Specifically, the refrigeration agent in compression chamber can flow into the cavity of housing upper by fluid passage, then discharge housing by exhaust port.Wherein, the lubricant oil of part separated process in the cavity of housing upper also can will fall back to the bottom oil sump of compressor via this fluid circulation passage.
Inventor finds, when the cross-section area of this fluid passage is too small, can produce excessive resistance to the discharge of refrigeration agent, the power consumption of compressor is increased.When the cross-section area of the fluid passage particularly between stator iron core and inner walls face is too small, the speed that refrigeration agent upwards flows will be excessive, the lubricant oil of separated process in the cavity of housing upper is fallen difficult, cause compressor oil sump oil starvation, thus affect the oil inside offering of compression chamber, cause the greasy property of compressor to worsen, produce the wearing and tearing between moving element.And when the cross-section area of fluid passage is excessive, the efficiency of motor can worsen, the power consumption of compressor also can be made to increase.
Therefore, present inventor has carried out special design in the fluid passage to the compressor adopting R290, makes the exhaust of the compressor of employing R290 more smooth and easy, and bottom oil sump also more easily got back to by lubricant oil simultaneously, and the lower power consumption of compressor, working efficiency can promote.
The present invention is intended to solve one of technical problem in correlation technique at least to a certain extent.For this reason, the present invention proposes a kind of compressor, described compressor air-discharging performance and greasy property good, low in energy consumption.
The invention allows for a kind of air-conditioning system with above-mentioned compressor.
According to the compressor of the embodiment of the present invention, comprising: housing, described housing has exhaust port, cylinder assembly, described cylinder assembly is located in described housing, and described cylinder assembly has compression chamber, electric machine assembly, described electric machine assembly is located in described housing, there is in described electric machine assembly the first fluid passage being communicated with described compression chamber and described exhaust port, second fluid passage is limited with between described electric machine assembly and described housing, the refrigeration agent that described compressor adopts is propane, described first fluid passage and the smallest cross-section area of described second fluid passage on the flow direction of described refrigeration agent are respectively G1 and G2, the discharge volume of described compressor is D, described G1, G2 and D meets relation: f=D × ρ d/G1, h=D × ρ d/G2, wherein, 0.1g/cm
2≤ f≤2.1g/cm
2, 0.06g/cm
2≤ h≤0.7g/cm
2, ρ d=0.038g/cm
3.
According to the compressor of the embodiment of the present invention, exhaust resistance is little, exhaust and oil return more smooth and easy, compressor low in energy consumption, lubricity is better, and operational efficiency improves and not easy to wear, compressor use safety and reliability.
In addition, compressor according to the above embodiment of the present invention can also have following additional technical characteristics:
According to one embodiment of present invention, when the rotating speed of described electric machine assembly is constant, 0.2g/cm
2≤ f≤2.1g/cm
2, 0.07g/cm
2≤ h≤0.35g/cm
2.
According to one embodiment of present invention, when the variable speed of described electric machine assembly, 0.1g/cm
2≤ f≤1.2g/cm
2, 0.06g/cm
2≤ h≤0.7g/cm
2.
According to one embodiment of present invention, described electric machine assembly comprises: stator, described stator is located in described housing, described with the spaced apart formation of the internal face of the described housing at least partially second fluid passage of the outer wall of described stator, is provided with the pilot hole of its thickness direction through in described stator; Rotor, described rotor is located in described pilot hole pivotly, the outer wall of described rotor and the described first fluid passage of the spaced apart formation of internal face of described stator.
According to one embodiment of present invention, described first fluid passage and described second fluid passage extend along the axis of described housing respectively.
According to one embodiment of present invention, described first fluid passage and described second fluid passage all constant at the cross-section area axially of described housing.
According to one embodiment of present invention, the outer wall of described stator is provided with trimming, being limited by the internal face of described trimming and described housing at least partially of described second fluid passage.
According to one embodiment of present invention, the outer wall of described stator is provided with groove, and a part for described second fluid passage is limited by the internal face of described groove and described housing.
According to one embodiment of present invention, described trimming and described groove comprise multiple respectively, and multiple described groove and multiple described trimming are along the spaced apart setting of circumference of described stator.
According to the air-conditioning system of the embodiment of the present invention, comprise the compressor according to the embodiment of the present invention.
Additional aspect of the present invention and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by practice of the present invention.
Accompanying drawing explanation
Fig. 1 is the structural representation of the compressor according to the embodiment of the present invention;
Fig. 2 is the structural representation of the electric machine assembly of compressor according to the embodiment of the present invention;
Fig. 3 is the schematic diagram of the first fluid passage of compressor according to the embodiment of the present invention;
Fig. 4 is the schematic diagram of the second fluid passage of compressor according to the embodiment of the present invention.
Reference character:
Compressor 100;
Housing 10; Exhaust port 11;
Cylinder assembly 20; Compression chamber 21; Cylinder 201; Bearing 202.
Electric machine assembly 30; First fluid passage 31; Second fluid passage 32; Stator 301; Pilot hole 3011; Trimming 3012; Groove 3013; Rotor 302.
Embodiment
Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.
The compressor 100 according to the embodiment of the present invention is described in detail below in conjunction with accompanying drawing.
Shown in Fig. 4, comprise housing 10, cylinder assembly 20 and electric machine assembly 30 according to the compressor 100 of the embodiment of the present invention.The refrigeration agent that compressor 100 adopts is propane, i.e. R290.
Cylinder assembly 20 and electric machine assembly 30 are located in housing 10 respectively.Housing 10 has exhaust port 11, and cylinder assembly 20 has compression chamber 21, has first fluid passage 31 in electric machine assembly 30, namely shown in Fig. 3 section line.First fluid passage 31 is communicated with compression chamber 21 and exhaust port 11, and refrigeration agent can flow to exhaust port 11 by first fluid passage 31.Be limited with second fluid passage 32 between electric machine assembly 30 and housing 10, namely shown in Fig. 4 section line, refrigeration agent also can flow to exhaust port 11 by second fluid passage 32.Wherein, the lubricant oil be separated with refrigeration agent can be back to bottom oil sump by two fluid passages, particularly second fluid passage 32.
Present inventor finds through research, and under identical refrigerating capacity, when adopting the refrigeration agent of R290, the flow-rate ratio refrigeration agent in the past of refrigeration agent is much smaller, and the flow of refrigeration agent is relevant with the discharge volume of compressor 100.Therefore, certain relation should be met between the cross-section area of two fluid passages in compressor 100 and the discharge volume of compressor 100.
Because the cross-section area of two fluid passages is along the flow direction of refrigeration agent being change, now, the flow of refrigeration agent then depends primarily on the minimum position of the cross-section area of two fluid passages.Therefore, certain relation should be met between the smallest cross-section area of two fluid passages and the discharge volume of compressor 100.
For convenience of describing, assuming that the discharge volume of compressor 100 is D.Assuming that first fluid passage 31 and the smallest cross-section area of second fluid passage 32 on the flow direction of refrigeration agent are respectively G1 and G2.That is, on the flow direction of the refrigeration agent in first fluid passage 31, the smallest cross-section area of this first fluid passage 31 is G1; On the flow direction of the refrigeration agent in second fluid passage 32, the smallest cross-section area of this second fluid passage 32 is G2.Wherein, the flow direction of refrigeration agent is the bearing of trend of fluid passage usually.
In addition, for convenience of describing, first fluid passage 31 described below or second fluid passage 32 smallest cross-section area all refer to smallest cross-section area on the flow direction of first fluid passage 31 or second fluid passage 32 refrigeration agent therein.
Inventor draws through research, and G1, G2 and D meet relation: f=D × ρ d/G1, h=D × ρ d/G2.Wherein, f and h is flow coefficient, 0.1g/cm
2≤ f≤2.1g/cm
2, 0.06g/cm
2≤ h≤0.7g/cm
2.ρ d is under the pressure (absolute pressure) of 1.88MPa, at the temperature of 70 DEG C, the density of R290 cryogen gaseous, ρ d=0.038g/cm
3.
Here, the discharge volume D of compressor 100 concrete condition of basis can carry out value, such as, in some embodiments of the invention, and 3.5cm
3≤ D≤65cm
3.When the value of D, f and h is determined, namely the smallest cross-section area S1 of first fluid passage 31 and second fluid passage 32 can determine.The exhaust performance meeting the compressor 100 of this relation is good, the lower power consumption of compressor 100, performance boost.
According to the compressor 100 of the embodiment of the present invention, certain relation is met respectively with the smallest cross-section area of second fluid passage 32 by making first fluid passage 31, make to adopt the exhaust resistance of the compressor 100 of R290 little, exhaust and oil return more smooth and easy, compressor 100 low in energy consumption, lubricity is better, and operational efficiency improves and not easy to wear, and compressor 100 uses safety and reliability.
Being understandable that, can be constant speed compressor according to the compressor 100 of the embodiment of the present invention, also can be frequency-changeable compressor.F and h can suitably adjust its span according to the type of compressor 100, and to improve the structure of compressor 100 more targetedly, make structural design more reasonable, the performance of compressor 100 is better.
Specifically, when compressor 100 is constant speed compressor, when namely the rotating speed of electric machine assembly 30 is constant, 0.2g/cm
2≤ f≤2.1g/cm
2, 0.07g/cm
2≤ h≤0.35g/cm
2; When compressor 100 is frequency-changeable compressor, namely when the variable speed of electric machine assembly 30,0.1g/cm
2≤ f≤1.2g/cm
2, 0.06g/cm
2≤ h≤0.7g/cm
2.
Shown in Fig. 4, electric machine assembly 30 can comprise stator 301 and rotor 302.Stator 301 can be located in housing 10, and be provided with the pilot hole 3011 of its thickness direction through in stator 301, rotor 302 is located in pilot hole 3011 pivotly.The thickness direction of usual stator 301 is the axis of stator 301, i.e. the axis of housing 10.The outer wall of rotor 302 and the internal face spaced apart formation first fluid passage 31 of stator 301, the internal face of stator 301 is the wall of pilot hole 3011.The outer wall of stator 301 at least partially with the internal face of housing 10 spaced apart formation second fluid passage 32.
Thus, refrigeration agent and lubricant oil can pass between stator 301 and rotor 302 and between stator 301 and housing 10, and the lubricity of electric machine assembly 30 is better, and gas flow is more disperseed smooth and easy, and exhaust efficiency is higher.
Preferably, first fluid passage 31 and second fluid passage 32 extend along the axis of housing 10 respectively.Thus, gas shorter and be easier to upwards flow by path, compressor 100 is vented more smooth and easy.Meanwhile, lubricant oil is easier to, and improves the utilization ratio of lubricant oil, and lubricity is better, and the power consumption of compressor 100 is lower.
According to some embodiments of the present invention, first fluid passage 31 is all constant at the cross-section area axially of housing 10 with second fluid passage 32.That is, first fluid passage 31 and second fluid passage 32 are formed as the constant structure of cross-section area on respective bearing of trend.Thus, refrigeration agent flows more steady in first fluid passage 31 and second fluid passage 32, and not easily turbulent flow occurs, the exhaust performance of compressor 100 is better.
According to some embodiments of the present invention, the outer wall of stator 301 can be provided with trimming 3012, can being limited by the internal face of trimming 3012 with housing 10 at least partially of second fluid passage 32.Further, the outer wall of stator 301 can also be provided with groove 3013, a part for second fluid passage 32 can be limited by the internal face of groove 3013 with housing 10.
In embodiment shown in Fig. 2 to Fig. 4, the outer wall of stator 301 had both been provided with trimming 3012, be provided with again groove 3013, a part for second fluid passage 32 is limited by the internal face of trimming 3012 with housing 10, and another part of second fluid passage 32 is limited by the internal face of groove 3013 with housing 10.Now, second fluid passage 32 is divided into multiple part, is dispersed passage.The smallest cross-section area sum of the smallest cross-section area of the wall that the smallest cross-section area of second fluid passage 32 is multiple groove 3013 and the internal face institute restriceted envelope of housing 10 and multiple trimming 3012 and the internal face institute restriceted envelope of housing 10.
Wherein, trimming 3012 and groove 3013 can comprise multiple respectively, and multiple groove 3013 and the circumference spaced apart setting of multiple trimming 3012 along stator 301, wherein the circumference of stator 301 is the circumference of housing 10.Preferably, multiple groove 3013 along the alternate setting of circumference of stator 301 with multiple trimming 3012, is provided with a trimming 3012 between two namely adjacent grooves 3013, is provided with a groove 3013 between two adjacent trimmings 3012.This kind of structural design is more reasonable, and the balance of compressor 100 is better, runs more reliable.
As shown in Figure 1, cylinder assembly 20 can comprise a cylinder 201, and cylinder 201 is provided with bearing 202.Air intake passage can be located on cylinder 201, and exhaust passage can be located on bearing 202.In the embodiment shown in fig. 1, compressor 100 is single cylinder compressor 100, certainly, the present invention is not limited thereto.Such as, in unshowned embodiments more of the present invention, compressor 100 can be duplex cylinder compressor 100, and namely comprise can two cylinders 201 for cylinder assembly 20.
Condenser, vaporizer and according to parts such as the compressors 100 of the embodiment of the present invention can be comprised according to the air-conditioning system of the embodiment of the present invention.This compressor 100 can be rolling rotor 302 compressor 100 as shown in Figure 1.Owing to having above-mentioned useful technique effect according to the compressor 100 of the embodiment of the present invention, therefore good according to the air-conditioning system exhaust performance of the embodiment of the present invention, the operational efficiency of refrigeration system is high, and Security improves.
To form according to other of the refrigeration system of the embodiment of the present invention and the linkage structure of operation and compressor 100 and miscellaneous part and annexation are known for the person of ordinary skill of the art, be not described in detail at this.
In describing the invention, it will be appreciated that, term " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " interior ", " outward ", " axis ", " radial direction ", orientation or the position relationship of the instruction such as " circumference " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore limitation of the present invention can not be interpreted as.
In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristics.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise one or more these features.In describing the invention, the implication of " multiple " is two or more, unless otherwise expressly limited specifically.
In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score can be that the first and second features directly contact, or the first and second features are by intermediary mediate contact.And, fisrt feature second feature " on ", " top " and " above " but fisrt feature directly over second feature or oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " can be fisrt feature immediately below second feature or tiltedly below, or only represent that fisrt feature level height is less than second feature.
In the present invention, unless otherwise clearly defined and limited, the term such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be mechanical connection, also can be electrical connection; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements.For the ordinary skill in the art, above-mentioned term concrete meaning in the present invention can be understood as the case may be.
In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can combine in one or more embodiment in office or example in an appropriate manner.In addition, when not conflicting, the feature of the different embodiment described in this specification or example and different embodiment or example can carry out combining and combining by those skilled in the art.
Although illustrate and describe embodiments of the invention above, be understandable that, above-described embodiment is exemplary, can not be interpreted as limitation of the present invention, and those of ordinary skill in the art can change above-described embodiment within the scope of the invention, revises, replace and modification.
Claims (10)
1. a compressor, is characterized in that, comprising:
Housing, described housing has exhaust port;
Cylinder assembly, described cylinder assembly is located in described housing, and described cylinder assembly has compression chamber;
Electric machine assembly, described electric machine assembly is located in described housing, has the first fluid passage being communicated with described compression chamber and described exhaust port, be limited with second fluid passage between described electric machine assembly and described housing in described electric machine assembly, the refrigeration agent that described compressor adopts is propane
Described first fluid passage and the smallest cross-section area of described second fluid passage on the flow direction of described refrigeration agent are respectively G1 and G2, the discharge volume of described compressor is D, and described G1, G2 and D meet relation: f=D × ρ d/G1, h=D × ρ d/G2, wherein, 0.1g/cm
2≤ f≤2.1g/cm
2, 0.06g/cm
2≤ h≤0.7g/cm
2, ρ d=0.038g/cm
3.
2. compressor according to claim 1, is characterized in that, when the rotating speed of described electric machine assembly is constant, and 0.2g/cm
2≤ f≤2.1g/cm
2, 0.07g/cm
2≤ h≤0.35g/cm
2.
3. compressor according to claim 1, is characterized in that, when the variable speed of described electric machine assembly, and 0.1g/cm
2≤ f≤1.2g/cm
2, 0.06g/cm
2≤ h≤0.7g/cm
2.
4. the compressor according to any one of claim 1-3, is characterized in that, described electric machine assembly comprises:
Stator, described stator is located in described housing, and described with the spaced apart formation of the internal face of the described housing at least partially second fluid passage of the outer wall of described stator, is provided with the pilot hole of its thickness direction through in described stator;
Rotor, described rotor is located in described pilot hole pivotly, the outer wall of described rotor and the described first fluid passage of the spaced apart formation of internal face of described stator.
5. compressor according to claim 4, is characterized in that, described first fluid passage and described second fluid passage extend along the axis of described housing respectively.
6. compressor according to claim 5, is characterized in that, described first fluid passage and described second fluid passage all constant at the cross-section area axially of described housing.
7. the compressor according to any one of claim 4-6, is characterized in that, the outer wall of described stator is provided with trimming, being limited by the internal face of described trimming and described housing at least partially of described second fluid passage.
8. compressor according to claim 7, is characterized in that, the outer wall of described stator is provided with groove, and a part for described second fluid passage is limited by the internal face of described groove and described housing.
9. compressor according to claim 8, is characterized in that, described trimming and described groove comprise multiple respectively, and multiple described groove and multiple described trimming are along the spaced apart setting of circumference of described stator.
10. an air-conditioning system, is characterized in that, comprises the compressor according to any one of claim 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510402156.7A CN105041651A (en) | 2015-07-09 | 2015-07-09 | Compressor and air-conditioning system with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510402156.7A CN105041651A (en) | 2015-07-09 | 2015-07-09 | Compressor and air-conditioning system with same |
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| Publication Number | Publication Date |
|---|---|
| CN105041651A true CN105041651A (en) | 2015-11-11 |
Family
ID=54448524
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|---|---|---|---|
| CN201510402156.7A Pending CN105041651A (en) | 2015-07-09 | 2015-07-09 | Compressor and air-conditioning system with same |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61280727A (en) * | 1985-05-17 | 1986-12-11 | Sanyo Electric Co Ltd | Hermetic motor compressor |
| EP1203159B1 (en) * | 1999-08-11 | 2005-03-02 | Toshiba Carrier Corporation | Compressor |
| CN100523509C (en) * | 2004-12-22 | 2009-08-05 | 日立空调·家用电器株式会社 | Rotary compressor |
| JP2011038485A (en) * | 2009-08-17 | 2011-02-24 | Panasonic Corp | Hermetic compressor |
| JP2013227971A (en) * | 2012-03-30 | 2013-11-07 | Daikin Industries Ltd | Compressor |
| CN204783667U (en) * | 2015-07-09 | 2015-11-18 | 广东美芝制冷设备有限公司 | Compressor and air conditioning system who has it |
-
2015
- 2015-07-09 CN CN201510402156.7A patent/CN105041651A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61280727A (en) * | 1985-05-17 | 1986-12-11 | Sanyo Electric Co Ltd | Hermetic motor compressor |
| EP1203159B1 (en) * | 1999-08-11 | 2005-03-02 | Toshiba Carrier Corporation | Compressor |
| CN100523509C (en) * | 2004-12-22 | 2009-08-05 | 日立空调·家用电器株式会社 | Rotary compressor |
| JP2011038485A (en) * | 2009-08-17 | 2011-02-24 | Panasonic Corp | Hermetic compressor |
| JP2013227971A (en) * | 2012-03-30 | 2013-11-07 | Daikin Industries Ltd | Compressor |
| CN204783667U (en) * | 2015-07-09 | 2015-11-18 | 广东美芝制冷设备有限公司 | Compressor and air conditioning system who has it |
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| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| CB03 | Change of inventor or designer information |
Inventor after: Chen Zhenhua Inventor after: Xiang Weimin Inventor after: Zhang Lifeng Inventor before: Chen Zhenhua |
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| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20151111 |