CN204783695U - Air conditioning system's compressor and air conditioning system who has this compressor - Google Patents
Air conditioning system's compressor and air conditioning system who has this compressor Download PDFInfo
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- CN204783695U CN204783695U CN201520499453.3U CN201520499453U CN204783695U CN 204783695 U CN204783695 U CN 204783695U CN 201520499453 U CN201520499453 U CN 201520499453U CN 204783695 U CN204783695 U CN 204783695U
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Abstract
The utility model discloses an air conditioning system's compressor and air conditioning system who has this compressor, the compressor includes: a housing. Establish the cylinder components in the casing, cylinder components have the compression chamber and with the suction channel of compression chamber intercommunication and with at least one exhaust passage of compression chamber intercommunication, the refrigerant that the compressor used is S1 as difluoromethane, the minimum cross -sectional area of suction channel on the flow direction of refrigerant, the minimum cross -sectional area sum of exhaust passage on the flow direction of refrigerant is S2, the discharge volume of compressor is D, S1 and D satisfy the relational expression: Y=D rho sS1, 0.12gcm2 <= y <= 0.45gcm2, rho s=0.028gcm3, S2 and D satisfy the relational expression: Z=D rho dS2, 1.15gcm2 <= z <= 2.85gcm2, rho d=0.079gcm3. According to the utility model discloses a compressor is breathed in and air discharge performance improves.
Description
Technical field
The utility model relates to air-conditioning technical field, more specifically, relates to a kind of compressor of air-conditioning system and has the air-conditioning system of this compressor.
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 R32 of one of refrigeration agent, i.e. difluoromethane as an alternative, for industry is paid close attention to.Its GWP is 675, is only about 1/3rd of R410A (GWP2100).Its safety class is A2L, flammable well below carbon-hydrogen refrigerant R290.Therefore, the product of application R32 refrigeration agent, in marketing and in the acceptance level of market, is better than R290 refrigerant product.But when the refrigeration agent used in air-conditioning changes, the structure of air-conditioning also should adjust.
Model utility content
The application makes the discovery of the following fact and problem and understanding based on inventor:
Inventor tests using the air-conditioning system of R32 refrigeration agent, find under air-conditioning ASHRAE test condition, no matter compressor is in suction condition or exhaust condition, adopt R32 refrigeration agent more much lower than the mass flow rate of R410A refrigeration agent, be about 65% ~ 75% of R410A 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, R32 refrigeration agent then exceeds about 20% than R410A refrigeration agent, specifically as shown in table 2.
Table 2
Because the latent heat of vaporization is higher, unit mass refrigerant suction or liberated heat more, therefore, although the R32 refrigeration agent shown in table 1 is more much lower than the mass flow rate of R410A refrigeration agent.But, under air-conditioning ASHRAE test condition, when compressor adopts identical discharge volume, adopt R32 refrigeration agent still can exceed about 5% ~ 7% than the refrigerating capacity of R410A refrigeration agent, specifically as shown in table 3:
Table 3
Therefore, obtain identical refrigerating capacity, the discharge volume of the compressor with rolling rotor of employing R32 refrigeration agent can than smaller during employing R410A refrigeration agent.
Meanwhile, inventor finds according to experimental study, and actual air-conditioning system, when mating, obtain suitable refrigerating capacity, adopts the filling quantity (quality) only needing 70% ~ 85% of R410A refrigeration agent in the past during R32 refrigeration agent.
In view of this, present inventor is specially for adopting the air-conditioning system of R32 refrigeration agent to be studied, and wherein improve the structure of compressor especially, make the compressor after improvement and air-conditioning system thereof can mate R32 refrigeration agent, usability is better.
Specifically, inventor finds, when the cross-section area of air intake passage is too small, then inhalation resistance increases, and the power consumption of compressor will rise; When the cross-section area of air intake passage is excessive, then air-breathing closing angle increases, and makes the gettering quantity of compressor reduce on the contrary, and refrigerating capacity worsens.
Similarly, when the cross-section area of exhaust passage is too small, then exhaust resistance increases, and the power consumption of compressor will rise; When the cross-section area of exhaust passage is excessive, then the volume of the pressurized gas in exhaust passage just increases, and this part volume will reflation, makes the air displacement of compressor reduce on the contrary, refrigerating capacity deterioration.
Therefore, present inventor has carried out special design to the air intake passage and exhaust passage that adopt the compressor of R32, and the pumping property of the compressor of employing R32 and exhaust performance are improved, and the working efficiency of compressor promotes.
The utility model is intended to solve one of technical problem in correlation technique at least to a certain extent.For this reason, the utility model proposes a kind of compressor, described compressor air suction performance and exhaust performance improve, and operational efficiency is high.
The utility model also proposed a kind of air-conditioning system with above-mentioned compressor.
According to compressor of the present utility model, comprising: housing; Cylinder assembly, described cylinder assembly is located in described housing, the air intake passage that described cylinder assembly has compression chamber and is communicated with described compression chamber, the refrigeration agent that described compressor adopts is difluoromethane, the smallest cross-section area of described air intake passage on the flow direction of described refrigeration agent is S1, the smallest cross-section area sum of described exhaust passage on the flow direction of described refrigeration agent is S2, the discharge volume of described compressor is D, described S1 and D meets relation: y=D × ρ s/S1, wherein, 0.12g/cm
2≤ y≤0.45g/cm
2, ρ s=0.028g/cm
3, described S2 and D meets relation: z=D × ρ d/S2, wherein, and 1.15g/cm
2≤ z≤2.85g/cm
2, ρ d=0.079g/cm
3.
According to compressor of the present utility model, pumping property and exhaust performance improve pumping property and improve and working efficiency lifting.
In addition, following additional technical characteristics can also be had according to compressor of the present utility model:
According to an embodiment of the present utility model, the second inspiratory limb that described air intake passage comprises the first inspiratory limb and is communicated with described first inspiratory limb, the outlet of described second inspiratory limb is towards described compression chamber, and the smallest cross-section area of described second intakeport section is described S1.
According to an embodiment of the present utility model, the second inspiratory limb is formed as cylindrical.
According to an embodiment of the present utility model, described first inspiratory limb and described second inspiratory limb are coaxially arranged.
According to an embodiment of the present utility model, on the flow direction of refrigeration agent, the cross-section area of described air intake passage is constant.
According to an embodiment of the present utility model, described exhaust passage is that the smallest cross-section area of at least two in multiple and multiple described exhaust passage is different.
According to an embodiment of the present utility model, described exhaust passage is that the smallest cross-section area of multiple and multiple described exhaust passage is all identical.
According to an embodiment of the present utility model, the cross section of each described exhaust passage is formed as circular respectively.
According to an embodiment of the present utility model, also comprise electric machine assembly, described housing has exhaust port, 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, 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, described G1, G2 and D meets relation: f=D × ρ d/G1, h=D × ρ d/G2, wherein, 0.2g/cm
2≤ f≤3.8g/cm
2, 0.12g/cm
2≤ h≤1.3g/cm
2, ρ d=0.079g/cm
3.
According to an embodiment of the present utility model, when the rotating speed of described electric machine assembly is constant, 0.4g/cm
2≤ f≤3.8g/cm
2, 0.14g/cm
2≤ h≤0.7g/cm
2.
According to an embodiment of the present utility model, when the variable speed of described electric machine assembly, 0.2g/cm
2≤ f≤2.2g/cm
2, 0.12g/cm
2≤ h≤1.3g/cm
2.
According to an embodiment of the present utility model, 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 an embodiment of the present utility model, described first fluid passage and described second fluid passage extend along the axis of described housing respectively.
According to an embodiment of the present utility model, described first fluid passage and described second fluid passage all constant at the cross-section area axially of described housing.
According to an embodiment of the present utility model, 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 an embodiment of the present utility model, 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 an embodiment of the present utility model, workpiece is provided with in described housing, described cylinder assembly forms a part for described workpiece, the filling quantity of the refrigeration agent of described air-conditioning system is R, the oil sealing amount of described compressor is L, the volume of described housing remaining internal cavities after installing described workpiece is C, L=MAX (L1, L2), wherein, L1=C/k ± 10 × D, L2=R × e, 0.6 × C≤R/ ρ+L2≤2.0 × C, 1.7≤k≤3.0,1.4≤e≤4.2, ρ=1.02g/cm
3.
According to an embodiment of the present utility model, when described compressor is constant speed compressor, 0.6 × C≤R/ ρ+L2≤1.4 × C, 1.7≤k≤2.6,1.4≤e≤3.1.
According to an embodiment of the present utility model, when described compressor is frequency-changeable compressor, 0.8 × C≤R/ ρ+L2≤2.0 × C, 1.9≤k≤3.0,1.8≤e≤4.2.
According to an embodiment of the present utility model, also comprise liquid-storage container, described liquid-storage container comprises shell and outer pipe, the outward opening end of described outer pipe to be positioned at outside described shell and to be communicated with described compression chamber, the inner opening end of described outer pipe is positioned at described shell, horizontal plane and the volume being positioned at the space that the described shell below this horizontal plane surrounds at described inner opening end place are the actual volume A of described liquid-storage container, the filling quantity of the refrigeration agent of described air-conditioning system is R, described A and R meets relation: A=R × m, wherein, 0.25≤m≤0.72.
According to an embodiment of the present utility model, described outer pipe is provided with the spill port being positioned at described shell, the horizontal plane at described spill port place is V with the volume being positioned at the space that the described shell under this horizontal plane surrounds, and the oil sealing amount of described compressor is L, wherein V/L≤0.2.
According to an embodiment of the present utility model, the vertical distance between described inner opening end and the roof of described shell is less than or equal to 1/3rd of the size that described shell vertically extends.
According to an embodiment of the present utility model, described cylinder assembly comprises a cylinder, and described air intake passage is located on described cylinder.
According to an embodiment of the present utility model, described cylinder block comprises cylinder and bearing, and described bearing is located at upper end and/or the lower end of described cylinder, being located at least partially on described bearing of described air intake passage.
According to an embodiment of the present utility model, described cylinder assembly comprises two cylinders, is provided with central diaphragm between two described cylinders, being located at least partially on described central diaphragm of described air intake passage.
According to air-conditioning system of the present utility model, comprise according to compressor of the present utility model.
Additional aspect of the present utility model 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 utility model.
Accompanying drawing explanation
Fig. 1 is the structural representation of the compressor of air-conditioning system according to the utility model embodiment;
Fig. 2 is the part-structure schematic diagram of the cylinder assembly of the compressor of air-conditioning system according to the utility model embodiment;
Fig. 3 is the structural representation of the air intake passage of the cylinder assembly of air-conditioning system according to the utility model first embodiment.
Fig. 4 is the structural representation of the air intake passage of the cylinder assembly of air-conditioning system according to the utility model second embodiment;
Fig. 5 is the structural representation of the air intake passage of the cylinder assembly of air-conditioning system according to the utility model the 3rd embodiment;
Fig. 6 is the structural representation of the air intake passage of the cylinder assembly of air-conditioning system according to the utility model the 4th embodiment;
Fig. 7 is the schematic diagram of the cylinder assembly of the compressor of air-conditioning system according to the utility model embodiment;
Fig. 8 is the structural representation of the electric machine assembly of the compressor of air-conditioning system according to the utility model embodiment;
Fig. 9 is the schematic diagram of the first fluid passage of the compressor of air-conditioning system according to the utility model embodiment;
Figure 10 is the schematic diagram of the second fluid passage of the compressor of air-conditioning system according to the utility model embodiment;
Figure 11 is the structural representation of the liquid-storage container of the compressor of air-conditioning system according to the utility model embodiment.
Reference character:
Compressor 100;
Housing 10;
Cylinder assembly 20; Compression chamber 21; Air intake passage 22; Exhaust passage 23; First inspiratory limb 221; Second inspiratory limb 222; 3rd inspiratory limb 223; 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;
Liquid-storage container 40; Shell 41; Outer pipe 42; Inner opening end 421; Outward opening end 422; Spill port 423.
Embodiment
Be described below in detail embodiment of the present utility model, 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 utility model, and can not be interpreted as restriction of the present utility model.
The compressor 100 according to the utility model embodiment is described in detail below in conjunction with accompanying drawing.
Shown in Figure 11, housing 10 and cylinder assembly 20 can be comprised according to the compressor 100 of the utility model embodiment.Cylinder assembly 20 can be located in housing 10.Cylinder assembly 20 has compression chamber 21, air intake passage 22 and at least one exhaust passage 23, air intake passage 22 is communicated with compression chamber 21, each exhaust passage 23 is also communicated with compression chamber 21, refrigeration agent can be drawn in compression chamber 21 by air intake passage 22, and the refrigeration agent in compression chamber 21 can be discharged by exhaust passage 23.Wherein, the refrigeration agent that compressor 100 adopts is difluoromethane, i.e. R32.
Present inventor finds through research, and under identical refrigerating capacity, when adopting the refrigeration agent of R32, 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, refrigeration agent enters between the cross-section area of the air intake passage 22 of compression chamber 21 processes and the discharge volume of compressor 100 and should meet certain relation.
Because the cross-section area of air intake passage 22 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 air intake passage 22.Therefore, certain relation should be met between the smallest cross-section area of air intake passage 22 and the discharge volume of compressor 100.
Same, refrigeration agent flows out between the cross-section area of the exhaust passage 23 of compression chamber 21 processes and the discharge volume of compressor 100 also should meet certain relation.Because the cross-section area of exhaust passage 23 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 exhaust passage 23.Simultaneously because exhaust passage 23 is not limited only to one, can have multiple.Therefore, certain relation should be met between the smallest cross-section area sum of exhaust passage 23 and the discharge volume of compressor 100.
For convenience of describing, suppose that the discharge volume of compressor 100 is D.Suppose that the smallest cross-section area of air intake passage 22 on the flow direction of refrigeration agent is S1.That is, on the flow direction of the refrigeration agent in air intake passage 22, the smallest cross-section area of this air intake passage 22 is S1.Wherein, the flow direction of refrigeration agent is the bearing of trend of air intake passage 22 usually.In addition, for convenience of describing, the smallest cross-section area of air intake passage 22 described below all refers to the smallest cross-section area on the flow direction of air intake passage 22 refrigeration agent therein.
Assuming that the smallest cross-section area sum of exhaust passage 23 on the flow direction of refrigeration agent is S2.That is, when exhaust passage 23 is one, on the flow direction of the refrigeration agent in this exhaust passage 23, the smallest cross-section area of this exhaust passage 23 is S2; When exhaust passage 23 is multiple, the smallest cross-section area sum of all exhaust passages 23 on the flow direction of each self-corresponding refrigeration agent is S2, in other words, S2 be after multiple smallest cross-section area is added and, the plurality of smallest cross-section area is respectively the smallest cross-section area of multiple exhaust passage 23 on the flow direction of separately inner refrigeration agent.
Wherein, the flow direction of refrigeration agent is the bearing of trend of exhaust passage 23 usually, and the flow direction of the refrigeration agent namely corresponding to each exhaust passage 23 is respective bearing of trend.In addition, for convenience of describing, the smallest cross-section area of exhaust passage 23 described below all refers to the smallest cross-section area on the flow direction of exhaust passage 23 refrigeration agent therein.
Inventor draws through research, and S1 and D meets relation: y=D × ρ s/S1.Wherein, y is inspiratory flow coefficient, 0.12g/cm
2≤ y≤0.45g/cm
2.ρ s is under the pressure (absolute pressure) of 1.1MPa, at the temperature of 18 DEG C, the density of R32 cryogen gaseous, ρ s=0.028g/cm
3.
Further, S2 and D meets relation: z=D × ρ d/S2.Wherein, z is extraction flow coefficient, 1.15g/cm
2≤ z≤2.85g/cm
2.ρ d is under the pressure (absolute pressure) of 3.5MPa, at the temperature of 90 DEG C, the density of R32 cryogen gaseous, ρ d=0.079g/cm
3.
Here, the discharge volume D of compressor 100 can carry out value as the case may be, such as, in embodiments more of the present utility model, and 3.0cm
3≤ D≤95cm
3.When the value of D and y is determined, namely the smallest cross-section area S1 of air intake passage 22 can determine.When the value of D and z is determined, namely the smallest cross-section area sum S2 of exhaust passage 23 can determine.The gettering efficiency and the exhaust efficiency that meet the compressor 100 of above-mentioned relation formula are better, the efficiengy-increasing of compressor 100.
According to the compressor 100 of the utility model embodiment, certain relation is met by making the smallest cross-section area of air intake passage 22, make the smallest cross-section area sum of exhaust passage 23 meet certain relation simultaneously, make the moderate dimensions of air intake passage 22 and exhaust passage 23, can not be excessive, also can not be too small, inhalation resistance and the exhaust resistance of the compressor 100 of employing R32 are little, air-breathing is moderate with exhaust, pumping property and exhaust performance improve, compressor 100 low in energy consumption, operational efficiency improves, and compressor 100 uses safety and reliability.
As shown in Figures 3 to 5, air intake passage 22 can comprise the first inspiratory limb 221 and the second inspiratory limb 222, second inspiratory limb 222 is communicated with the first inspiratory limb 221.The outlet of the second inspiratory limb 222 is towards compression chamber 21.That is, one end away from the first inspiratory limb 221 of the second inspiratory limb 222 is communicated with compression chamber 21, arranges away from compression chamber 21 compared to the second inspiratory limb 222, first inspiratory limb 221.Refrigeration agent first through the first inspiratory limb 221, then through the second inspiratory limb 222, finally enters into compression chamber 21.
Wherein, the smallest cross-section area of the second inspiratory limb 222 is S1.That is, the actual inspiratory limb depended near compression chamber 21 of the flowing of refrigeration agent in air intake passage 22.Because refrigeration agent flow velocity when flowing through the smallest cross-sectional place of the second inspiratory limb 222 is relatively very fast, make refrigeration agent be easier to be inhaled in compression chamber 21, the pumping property of compressor 100 is good.
Be understandable that, the shape of the second inspiratory limb 222 can be formed as multiple.Such as, as shown in Figure 3, according to embodiments more of the present utility model, on the flow direction of refrigeration agent, the cross-section area of the second inspiratory limb 222 can be constant.That is, the cross-section area of the second inspiratory limb 222 cutting is at an arbitrary position S1, and this value remains unchanged.Wherein, the flow direction of refrigeration agent is the axis of the second inspiratory limb 222, i.e. direction shown in dotted lines in Figure 3.
Certainly, the shape of the second inspiratory limb 222 is not limited thereto.Alternatively, in embodiments more of the present utility model, the cross-section area of the second inspiratory limb 222 can reduce gradually along the flow direction of refrigeration agent, also can increase gradually.Now, the smallest cross-section area S1 of the second inspiratory limb 222 is then the cross-section area of wherein one end of the second inspiratory limb 222.Such as, as shown in Figure 4, on the flow direction of refrigeration agent, the cross-section area of the second inspiratory limb 222 increases gradually.Now, the smallest cross-section area S1 of the second inspiratory limb 222 is the cross-section area of one end away from compression chamber 21 of the second inspiratory limb 222.
In preferred embodiments more of the present utility model, the second inspiratory limb 222 is formed as cylindrical.That is, the second inspiratory limb 222 extends straight, and the cross-section area of the second inspiratory limb 222 is formed as circular, and is remaining unchanged along this cross-section area on the flow direction of refrigeration agent.Thus, the flow resistance of refrigeration agent is less, and flow more smooth and easy and not easily turbulent flow occur, the air suction and noise of compressor 100 is little.
Preferably, the first inspiratory limb 221 and the second inspiratory limb 222 are coaxially arranged.That is, the central axis of the first inspiratory limb 221 and the central axis of the second inspiratory limb 222 are located along the same line.Thus, can roughly linearly flow in the process of refrigeration agent flowing in compression chamber 21, the flowing of refrigeration agent is more smooth and easy and not easily turbulent flow occurs, the inhalation resistance of compression chamber 21 is little, refrigeration agent more easily enters compression chamber 21, and the pumping property of compressor 100 is good, and air suction and noise is less.
Be understandable that, the first inspiratory limb 221 can directly be communicated with the second inspiratory limb 222, also can indirect communication.Such as, in the embodiment shown in Fig. 3 and Fig. 4, the first inspiratory limb 221 is with the second inspiratory limb 222 and is directly communicated with.Again such as, in the embodiment shown in fig. 5, the first inspiratory limb 221 and the second inspiratory limb 222 indirect communication.Specifically, air intake passage 22 can also comprise the 3rd inspiratory limb the 223, three inspiratory limb 223 between the first inspiratory limb 221 and the first inspiratory limb 221.
That is, the first inspiratory limb 221 is not directly connected with the second inspiratory limb 222, but is connected by the second inspiratory limb 222 indirect transition.Refrigeration agent successively through the first inspiratory limb 221, the 3rd inspiratory limb 223 and the second inspiratory limb 222, can enter into compression chamber 21.Due to, the 3rd inspiratory limb 223 plays the effect of connection first inspiratory limb 221 and the second inspiratory limb 222, and therefore, in reality manufactures, the length of the 3rd inspiratory limb 223 can be very short.
Wherein, on the flow direction of refrigeration agent, the shaft shoulder shape structure that can be diminished gradually by cross-section area between two adjacent inspiratory limb carries out transition.Thus, be not only convenient to manufacture, and refrigeration agent can be made to flow steadily during transition flow between inspiratory limb, not easily turbulent flow occurs.
In addition, as shown in Figure 6, on the flow direction of refrigeration agent, the cross-section area of air intake passage 22 can be constant.In other words, when air intake passage 22 is made up of multiple inspiratory limb such as the first inspiratory limb 221, second inspiratory limb 222 and the 3rd inspiratory limb 223, multiple inspiratory limb is all identical along the cross-section area on the flow direction of refrigeration agent, and the smallest cross-section area S1 of air intake passage 22 is the cross-section area of any position of air intake passage 22.Thus, refrigeration agent flows more steady in air intake passage 22, and not easily turbulent flow occurs, compressor 100 inspiratory effects is good.
According to embodiments more of the present utility model, exhaust passage 23 can be multiple, and the refrigeration agent in compression chamber 21 can discharge cylinder assembly 20 by multiple exhaust passage 23.The exhaust efficiency of compressor 100 can be improved thus.Alternatively, the smallest cross-section area of at least two in multiple exhaust passage 23 is different.That is, when exhaust passage 23 has multiple, the smallest cross-section area of all exhaust passages 23 can be all not identical, wherein the smallest cross-section area of portion discharge passage 23 also can be had to be identical.
Certainly, the utility model is not limited thereto, and such as, the smallest cross-section area of multiple exhaust passage 23 is all identical, and the smallest cross-section area of namely all exhaust passages 23 can be all identical.Thus, more even when compression chamber 21 is outwards vented, exhaust effect is better.
According to a concrete example of the present utility model, the cross-section area of each exhaust passage 23 is constant on the flow direction of refrigeration agent.That is, all exhaust passages 23 remain unchanged on the flow direction of each self-corresponding refrigeration agent.Thus, refrigeration agent flows more steady in exhaust passage 23, and not easily turbulent flow occurs, the exhaust performance of compressor 100 is better.
Preferably, the cross section of each exhaust passage 23 is formed as circular respectively.Thus, the internal face of exhaust passage 23 is comparatively round and smooth, and refrigeration agent flow resistance in exhaust passage 23 is less, and compressor 100 is vented more smooth and easy, and exhaust noise is less.
With reference to shown in Fig. 1, comprise housing 10, cylinder assembly 20 and electric machine assembly 30 according to the compressor 100 of the utility model embodiment.The refrigeration agent that compressor 100 adopts is difluoromethane, i.e. R32.
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. 9 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 Figure 10 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 R32, 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, 0.2g/cm
2≤ f≤3.8g/cm
2, 0.12g/cm
2≤ h≤1.3g/cm
2.ρ d is under the pressure (absolute pressure) of 3.5MPa, at the temperature of 90 DEG C, the density of R32 cryogen gaseous, ρ d=0.079g/cm
3.
Here, the discharge volume D of compressor 100 concrete condition of basis can carry out value, such as, in embodiments more of the present utility model, and 3.0cm
3≤ D≤95cm
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 utility model embodiment, 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 R32 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 utility model embodiment, 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, 0.4g/cm
2≤ f≤3.8g/cm
2, 0.14g/cm
2≤ h≤0.7g/cm
2; When compressor 100 is frequency-changeable compressor, namely when the variable speed of electric machine assembly 30,0.2g/cm
2≤ f≤2.2g/cm
2, 0.12g/cm
2≤ h≤1.3g/cm
2.
With reference to shown in Fig. 1 and Fig. 8 to Figure 10, 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 embodiments more of the present utility model, 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 embodiments more of the present utility model, 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. 8 to Figure 10, 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.
Present inventor finds through research, interrelated between the enclosed volume of the filling quantity of the refrigeration agent of air-conditioning system and the lubricant oil of compressor 100 inside.For guaranteeing the reliability of compressor 100, between the enclosed volume of the filling quantity of the refrigeration agent of air-conditioning system and the lubricant oil of compressor 100 inside, certain relation should be met.
For convenience of describing, assuming that the filling quantity of the refrigeration agent of the air-conditioning system at this compressor 100 place is R, the oil sealing amount of compressor 100 is L, and the amount of lubricant oil that namely compressor 100 inside is enclosed is L.The volume of the internal cavities that housing 10 is remaining after installment work parts is C, and after the volume of inner space that namely housing 10 surrounds deducts the volume of the assembly in housing 10, remaining volume is C.
Inventor draws through research, L=MAX (L1, L2), wherein, and L1=C/k ± 10 × D, L2=R × e, 0.6 × C≤R/ ρ+L2≤2.0 × C.Wherein, k and e is coefficient, 1.7≤k≤3.0,1.4≤e≤4.2.ρ is the density of the R32 coolant liquid at temperature is-10 DEG C, ρ=1.02g/cm
3.
Here, the discharge volume D of the compressor 100 and filling quantity R of refrigeration agent the concrete condition of basis can carry out value, such as, in embodiments more of the present utility model, and 3.0cm
3≤ D≤95cm
3, 120g≤R≤5500g.When the value of D, R, k and e is determined, namely the oil sealing amount L of compressor 100 can determine.The greasy property meeting the compressor 100 of this relation is good, the efficiengy-increasing of compressor 100, and energy consumption reduces.
According to the compressor 100 of the utility model embodiment, oil sealing amount is arranged rationally, and make the greasy property of compressor 100 good, energy consumption is low, not easy to wear during operation, and the high and long service life of working efficiency, compressor 100 uses safety and reliability.
Being understandable that, can be constant speed compressor 100 according to the compressor 100 of the utility model embodiment, also can be frequency-changeable compressor 100.The span of parameter suitably can adjust according to the type of compressor 100 above, 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 100,0.6 × C≤R/ ρ+L2≤1.4 × C, 1.7≤k≤2.6,1.4≤e≤3.1.When compressor 100 is frequency-changeable compressor 100,0.8 × C≤R/ ρ+L2≤2.0 × C, 1.9≤k≤3.0,1.8≤e≤4.2.
With reference to shown in Fig. 1 and Figure 11, liquid-storage container 40 comprises shell 41 and outer pipe 42, and outer pipe 42 has two ends, is respectively outward opening end 422 and inner opening end 421.The outward opening end 422 of outer pipe 42 to be positioned at outside shell 41 and to be communicated with compression chamber 21, and the inner opening end 421 of outer pipe 42 is positioned at shell 41.
Capacity due to liquid-storage container 40 relates to its problem holding how many liquid refrigerants.When in air-conditioning system, the filling quantity of refrigeration agent has lacked, so the capacity of liquid-storage container 40 also needs to make to optimize and revise.In liquid-storage container 40, the liquid level height of liquid refrigerant can not exceed the horizontal plane at inner opening end 421 place of outer pipe 42.The inner space that shell 41 surrounds can not all for storing, and wherein only segment space plays conclusive effect.This segment space is the actual volume of liquid-storage container 40.
Specifically, horizontal plane and the volume being positioned at the space that the shell 41 below this horizontal plane surrounds at inner opening end 421 place are the actual volume A of liquid-storage container 40.That is, the actual volume A of liquid-storage container 40 is through horizontal plane and the volume being positioned at the space that the shell 41 below this horizontal plane surrounds of inner opening end 421.Suppose that the filling quantity of the refrigeration agent of air-conditioning system is R.
Inventor finds through research, and A and R meets relation: A=R × m.Wherein, m is coefficient, 0.25≤m≤0.72.When the structure of liquid-storage container 40 meets this relation, liquid-storage container 40 can make liquid refrigerant transform in time to gaseous refrigerant, avoids liquid refrigerant to enter compression chamber 21, ensures the ride quality of compressor 100.
Here, the filling quantity R of refrigeration agent the concrete condition of basis can carry out value, such as, in embodiments more of the present utility model, and 120g≤R≤5500g.When the value of R and m is determined, namely the actual volume A of compressor 100 can determine.Satisfactory liquid-storage container 40 can be manufactured according to this actual volume A.
According to the compressor 100 of the utility model embodiment, the actual volume of liquid-storage container 40 can be determined according to the relation determined, liquid-storage container 40 not only can ensure the normal storage of liquid refrigerant, and can make liquid refrigerant before flowing out liquid-storage container 40, be converted into the refrigeration agent of gaseous state in time, liquid refrigeration agent is avoided to enter into compression chamber 21 from outer pipe 42, liquid refrigeration agent is avoided to cause damage to compressor 100, compressor 100 is safe and reliable to operation, favorable working performance, long service life.
As shown in figure 11, outer pipe 42 is provided with the spill port 423 being positioned at shell 41.That is, spill port 423 is located in the part being positioned at shell 41 of outer pipe 42, and the lubricant oil in liquid-storage container 40 can be got back in compressor 100 by this spill port 423.Assuming that the oil sealing amount of compressor 100 is L, the horizontal plane supposing spill port 423 place and the volume being positioned at the space that the shell 41 under this horizontal plane surrounds are V.
Under some operating mode (such as worst hot case), when liquid-storage container 40 inside does not exist liquid refrigerant, what this space stored is lubricant oil; (such as worst cold case under some operating mode, deposition promoter operating mode), when there is liquid refrigerant and lubricant oil in liquid-storage container 40 inside simultaneously, due to below 40 DEG C time, liquid refrigerant is than lubricant oil weight, therefore according to the difference of amount of liquid refrigerant, what this space stored can be refrigeration agent, also can contain refrigeration agent and lubricant oil simultaneously.When this space store be refrigeration agent or lubricant oil time, both do not participate in the circulation of refrigeration system, therefore can be described as and be wasted.
Therefore, when the filling quantity of refrigeration agent in air-conditioning system and the oil sealing amount of compressor 100 have adjusted, the volume V in this space also needs to optimize and revise.Inventor finds through research, should meet following relationship: wherein V/L≤0.2 between the volume V in this space and the oil sealing amount L of compressor 100.When the structure of liquid-storage container 40 meets this relation, lubricant oil in liquid-storage container 40 can by spill port 423 oil return in time, reduce the hold-up of lubricant oil in liquid-storage container 40, improve the utilization ratio of lubricant oil, also can ensure that liquid refrigerant gasifies in time simultaneously, improve compressor 100 reliability of operation.
Here, the oil sealing amount L of compressor 100 concrete condition of basis can carry out value, such as, in embodiments more of the present utility model, and 80ml≤L≤1600ml.When the value of L is determined, namely the volume V in this space can determine.The greasy property meeting the compressor 100 of this relation is good, the efficiengy-increasing of compressor 100, and energy consumption reduces.Here, it should be noted that, the value of the oil sealing amount L of compressor also can be determined according to relation above, and namely the scope of L for choose between L1 and L2.
According to embodiments more of the present utility model, the vertical distance d1 between the roof of inner opening end 421 and shell 41 is less than or equal to 1/3rd of the size d2 that shell 41 vertically extends.As shown in Figure 2, the vertical distance d1 between the roof of inner opening end 421 and shell 41 is less than 1/3rd of the size d2 that shell 41 vertically extends.Thus, the inner space of liquid-storage container 40 can better be utilized, and the memory space of liquid refrigerant is large and gaseous refrigerant is discharged smooth and easy, and the usability of liquid-storage container 40 is good.
Here, it should be noted that, when the roof of liquid-storage container 40 is formed as plane, the vertical distance d1 between inner opening end 421 and roof is the vertical distance between any position of roof and inner opening end 421; When the roof of liquid-storage container 40 is formed as the arc shaped surface projected upwards, the vertical distance d1 between inner opening end 421 and roof is the vertical distance between the arc center of roof and inner opening end 421.
As shown in figure 11, the part that outer pipe 42 is positioned at shell 41 vertically extends.Thus, be not only beneficial to the flowing of gaseous refrigerant in outer pipe 42, and the size of outer pipe 42 is relatively shorter, material consumption is less.Preferably, the part being positioned at shell 41 of outer pipe 42 can be located at the position of the medial axis of housing 10, is beneficial to refrigeration agent and evenly flows into outer pipe 42 from surrounding.
As shown in Figure 1, cylinder assembly 20 can comprise a cylinder 201, and air intake passage 22 can be located on cylinder 201.Certainly, the structure of cylinder assembly 20 is not limited only to this, and such as, cylinder assembly 20 can comprise cylinder 201 and bearing 202, and bearing 202 can be located at upper end and/or the lower end of cylinder 201.Such as, when bearing 202 is one, this bearing 202 can also can for being located at the lower bearing of cylinder 201 lower end for the upper bearing (metal) being located at cylinder 201 upper end; When bearing 202 is two, two bearings 202 can be respectively upper bearing (metal) and lower bearing.
Wherein, air intake passage 22 can be located on bearing 202 at least partially.That is, air intake passage 22 can be located on bearing 202 completely, also can partly be located on bearing 202.When air intake passage 22 is located on bearing 202 completely, the opening of air intake passage 22 is directly communicated with compression chamber 21.When air intake passage 22 part is located on bearing 202, another part of air intake passage 22 still can be located on cylinder 201.Wherein, compression chamber 21 can directly directly be communicated with the air intake passage 22 be positioned on bearing 202, and also directly can be communicated with the air intake passage 22 be positioned on cylinder 201, this can be arranged as the case may be.
Alternatively, in unshowned embodiments more of the present utility model, cylinder assembly 20 can comprise two cylinders 201.That is, can be duplex cylinder compressor 100 according to the compressor 100 of the utility model embodiment.Be provided with central diaphragm between two cylinders 201, air intake passage 22 can be located on central diaphragm at least partially.That is, air intake passage 22 can all be located on central diaphragm, also can partly be located on central diaphragm.
When air intake passage 22 is located on central diaphragm completely, the compression chamber 21 of two cylinders 201 directly can be communicated with the opening of air intake passage 22 respectively.When air intake passage 22 part is located on central diaphragm, another part of air intake passage 22 can be located on cylinder 201, and when cylinder assembly 20 also has bearing 202, another part of air intake passage 22 also can be located on bearing 202.Wherein, compression chamber 21 can directly directly be communicated with the air intake passage 22 be positioned on central diaphragm, and also directly can be communicated with the air intake passage 22 be positioned on cylinder 201 or bearing 202, this can be arranged as the case may be.
Condenser, vaporizer and according to parts such as the compressors 100 of the utility model embodiment can be comprised according to the air-conditioning system of the utility model embodiment.This compressor 100 can be compressor with rolling rotor as shown in Figure 1.Owing to having above-mentioned useful technique effect according to the compressor 100 of the utility model embodiment, therefore good according to the air-conditioning system pumping property of the utility model embodiment, the operational efficiency of refrigeration system is high, and Security improves.
To form according to other of the refrigeration system of the utility model embodiment 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 description of the present utility model, 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 utility model and simplified characterization for convenience of description, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore can not be interpreted as restriction of the present utility model.
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 description of the present utility model, the implication of " multiple " is two or more, unless otherwise expressly limited specifically.
In the utility model, 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 " 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 " 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 utility model, 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, the concrete meaning of above-mentioned term in the utility model 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 utility model 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 described embodiment of the present utility model above, be understandable that, above-described embodiment is exemplary, can not be interpreted as restriction of the present utility model, those of ordinary skill in the art can change above-described embodiment, revises, replace and modification in scope of the present utility model.
Claims (26)
1. a compressor for air-conditioning system, is characterized in that, comprising:
Housing;
Cylinder assembly, described cylinder assembly is located in described housing, described cylinder assembly has compression chamber and the air intake passage that is communicated with described compression chamber and at least one exhaust passage be communicated with described compression chamber, the refrigeration agent that described compressor adopts is difluoromethane, the smallest cross-section area of described air intake passage on the flow direction of described refrigeration agent is S1, the smallest cross-section area sum of described exhaust passage on the flow direction of described refrigeration agent is S2, and the discharge volume of described compressor is D
Described S1 and D meets relation: y=D × ρ s/S1, wherein, and 0.12g/cm
2≤ y≤0.45g/cm
2, ρ s=0.028g/cm
3, described S2 and D meets relation: z=D × ρ d/S2, wherein, and 1.15g/cm
2≤ z≤2.85g/cm
2, ρ d=0.079g/cm
3.
2. the compressor of air-conditioning system according to claim 1, it is characterized in that, the second inspiratory limb that described air intake passage comprises the first inspiratory limb and is communicated with described first inspiratory limb, the outlet of described second inspiratory limb is towards described compression chamber, and the smallest cross-section area of described second inspiratory limb is described S1.
3. the compressor of air-conditioning system according to claim 2, is characterized in that, the second inspiratory limb is formed as cylindrical.
4. the compressor of air-conditioning system according to claim 2, is characterized in that, described first inspiratory limb and described second inspiratory limb are coaxially arranged.
5. the compressor of air-conditioning system according to claim 1, is characterized in that, on the flow direction of refrigeration agent, the cross-section area of described air intake passage is constant.
6. the compressor of air-conditioning system according to claim 1, is characterized in that, described exhaust passage is that the smallest cross-section area of at least two in multiple and multiple described exhaust passage is different.
7. the compressor of air-conditioning system according to claim 1, is characterized in that, described exhaust passage is that the smallest cross-section area of multiple and multiple described exhaust passage is all identical.
8. the compressor of air-conditioning system according to claim 1, is characterized in that, the cross section of each described exhaust passage is formed as circular respectively.
9. the compressor of air-conditioning system according to claim 1, it is characterized in that, also comprise electric machine assembly, described housing has exhaust port, 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, 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, described G1, G2 and D meets relation: f=D × ρ d/G1, h=D × ρ d/G2, wherein, 0.2g/cm
2≤ f≤3.8g/cm
2, 0.12g/cm
2≤ h≤1.3g/cm
2, ρ d=0.079g/cm
3.
10. the compressor of air-conditioning system according to claim 9, is characterized in that, when the rotating speed of described electric machine assembly is constant, and 0.4g/cm
2≤ f≤3.8g/cm
2, 0.14g/cm
2≤ h≤0.7g/cm
2.
The compressor of 11. air-conditioning systems according to claim 9, is characterized in that, when the variable speed of described electric machine assembly, and 0.2g/cm
2≤ f≤2.2g/cm
2, 0.12g/cm
2≤ h≤1.3g/cm
2.
The compressor of 12. air-conditioning systems according to claim 9, 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.
The compressor of 13. air-conditioning systems according to claim 9, is characterized in that, described first fluid passage and described second fluid passage extend along the axis of described housing respectively.
The compressor of 14. air-conditioning systems according to claim 9, is characterized in that, described first fluid passage and described second fluid passage all constant at the cross-section area axially of described housing.
The compressor of 15. air-conditioning systems according to claim 12, 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.
The compressor of 16. air-conditioning systems according to claim 15, 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.
The compressor of 17. air-conditioning systems according to claim 1, it is characterized in that, workpiece is provided with in described housing, described cylinder assembly forms a part for described workpiece, the filling quantity of the refrigeration agent of described air-conditioning system is R, the oil sealing amount of described compressor is L, and the volume of described housing remaining internal cavities after installing described workpiece is C, L=MAX (L1, L2), wherein, L1=C/k ± 10 × D, L2=R × e, 0.6 × C≤R/ ρ+L2≤2.0 × C, 1.7≤k≤3.0,1.4≤e≤4.2, ρ=1.02g/cm
3.
The compressor of 18. air-conditioning systems according to claim 17, is characterized in that, when described compressor is constant speed compressor, and 0.6 × C≤R/ ρ+L2≤1.4 × C, 1.7≤k≤2.6,1.4≤e≤3.1.
The compressor of 19. air-conditioning systems according to claim 17, is characterized in that, when described compressor is frequency-changeable compressor, and 0.8 × C≤R/ ρ+L2≤2.0 × C, 1.9≤k≤3.0,1.8≤e≤4.2.
The compressor of 20. air-conditioning systems according to claim 1, it is characterized in that, also comprise liquid-storage container, described liquid-storage container comprises shell and outer pipe, the outward opening end of described outer pipe to be positioned at outside described shell and to be communicated with described compression chamber, the inner opening end of described outer pipe is positioned at described shell, horizontal plane and the volume being positioned at the space that the described shell below this horizontal plane surrounds at described inner opening end place are the actual volume A of described liquid-storage container, the filling quantity of the refrigeration agent of described air-conditioning system is R, described A and R meets relation: A=R × m, wherein, 0.25≤m≤0.72.
The compressor of 21. air-conditioning systems according to claim 20, it is characterized in that, described outer pipe is provided with the spill port being positioned at described shell, the horizontal plane at described spill port place is V with the volume being positioned at the space that the described shell under this horizontal plane surrounds, the oil sealing amount of described compressor is L, wherein V/L≤0.2.
The compressor of 22. air-conditioning systems according to claim 20, is characterized in that, the vertical distance between described inner opening end and the roof of described shell is less than or equal to 1/3rd of the size that described shell vertically extends.
The compressor of 23. air-conditioning systems according to claim 1, is characterized in that, described cylinder assembly comprises a cylinder, and described air intake passage is located on described cylinder.
The compressor of 24. air-conditioning systems according to claim 1, is characterized in that, described cylinder block comprises cylinder and bearing, and described bearing is located at upper end and/or the lower end of described cylinder, being located at least partially on described bearing of described air intake passage.
The compressor of 25. air-conditioning systems according to claim 1, is characterized in that, described cylinder assembly comprises two cylinders, is provided with central diaphragm between two described cylinders, being located at least partially on described central diaphragm of described air intake passage.
26. 1 kinds of air-conditioning systems, is characterized in that, comprise the compressor of the air-conditioning system according to any one of claim 1-25.
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| CN201520499453.3U CN204783695U (en) | 2015-07-09 | 2015-07-09 | Air conditioning system's compressor and air conditioning system who has this compressor |
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|---|---|---|---|
| CN201520499453.3U CN204783695U (en) | 2015-07-09 | 2015-07-09 | Air conditioning system's compressor and air conditioning system who has this compressor |
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| Publication Number | Publication Date |
|---|---|
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104976125A (en) * | 2015-07-09 | 2015-10-14 | 广东美芝制冷设备有限公司 | Compressor of air conditioner system and air conditioner system with compressor |
| CN110863990A (en) * | 2019-11-19 | 2020-03-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and air conditioner |
-
2015
- 2015-07-09 CN CN201520499453.3U patent/CN204783695U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104976125A (en) * | 2015-07-09 | 2015-10-14 | 广东美芝制冷设备有限公司 | Compressor of air conditioner system and air conditioner system with compressor |
| CN110863990A (en) * | 2019-11-19 | 2020-03-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and air conditioner |
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Granted publication date: 20151118 Termination date: 20190709 |