CN209724658U

CN209724658U - Rotary compressor

Info

Publication number: CN209724658U
Application number: CN201920326215.0U
Authority: CN
Inventors: 乐红胜; 黄之敏; 谢郦卿; 杨贝
Original assignee: Shanghai Highly Electrical Appliances Co Ltd
Current assignee: Shanghai Highly Electrical Appliances Co Ltd
Priority date: 2019-03-14
Filing date: 2019-03-14
Publication date: 2019-12-03
Anticipated expiration: 2029-03-14

Abstract

This application provides a kind of rotary compressors, comprising: electric machine assembly, compression assembly and crankshaft；Electric machine assembly includes stator and rotor, and rotor is rotatablely arranged in stator；Compression assembly includes the first cylinder and the second cylinder, is provided with piston and blade in the first cylinder and the second cylinder；One end of crankshaft and the rotor of electric machine assembly connect, and the other end of crankshaft is protruded into the first cylinder and the second cylinder and connect with piston；Wherein, the discharge capacity of rotary compressor is between 50.0cc~59.0cc, and the volume of stator is in 110cm³To 160cm³Between, the outer diameter of stator is between 130mm to 145mm.In rotary compressor provided by the present application, by the ratio for controlling the outer diameter of the volume of stator and the ratio of outer diameter and the height of blade and stator of outer diameter, the eccentricity of crankshaft and stator, so that rotary compressor is while reducing size and weight, its refrigerating capacity is kept, to realize the requirement of miniaturization.

Description

Rotary compressor

Technical field

This application involves a kind of compressor, in particular to a kind of rotary compressor.

Background technique

In general, compressor converts electrical current into kinetic energy, and refrigerant is compressed using kinetic energy.It is pressed according to refrigerant The mode of contracting, compressor can be divided into rotary compressor (rotary compressor), turbo-compressor (scroll Compressor), the multiple types such as reciprocation type compressor (reciprocal compressor).

In the development process of rotary compressor, miniaturization is a kind of trend.However, the compressor of small shell diameter is freezing Water identical with the compressor of large shell caliber is unable to reach in ability and COP (Coefficiency of Performance) index It is flat.Therefore, powerful rotary compressor is generally all developed on large shell caliber.For example, being widely used in 5HP heat pump heating unit And the rotary constant speed compressor of commercial heat pump water-heater system, the refrigerant used for R410A, discharge capacity 50.0cc~ Between 59.0cc, the outer diameter of stator has been more than 150mm.It is well known that the outer diameter of stator is bigger, the volume of compressor It is bigger, weight is heavier, correspondingly, the manufacturing cost of compressor is higher.Currently, the powerful generally existing body of rotary compressor Long-pending and weight is excessive, and the excessively high problem of manufacturing cost is unable to satisfy the requirement of miniaturization.

Base this, the volume and weight for how solving existing powerful rotary compressor is excessive, it is small-sized to be unable to satisfy The requirement of change, at those skilled in the art's technical problem urgently to be resolved.

Utility model content

For the defects in the prior art, it the purpose of this utility model is to provide a kind of rotary compressor, overcomes The difficulty of the prior art can effectively reduce the size and weight of constant speed compressor while guaranteeing refrigerating capacity, realize The requirement of miniaturization substantially reduces the manufacturing cost of compressor.

One aspect according to the present utility model provides a kind of rotary compressor, comprising: electric machine assembly, compression assembly And crankshaft；

The electric machine assembly includes stator and rotor, and the rotor is rotatablely arranged in the stator；

The compression assembly includes the first cylinder and the second cylinder, is provided with work in first cylinder and the second cylinder Plug and blade；

One end of the crankshaft is connect with the rotor of the electric machine assembly, and the other end of the crankshaft protrudes into first gas It is connect in cylinder and the second cylinder and with the piston；

Wherein, between 50.0cc~59.0cc, the volume of the stator exists the discharge capacity of the rotary compressor 110cm³To 160cm³Between, the outer diameter of the stator is between 130mm to 145mm.

Optionally, the ratio of the outer diameter of the eccentricity of the crankshaft and the stator is between 0.023 to 0.051, The ratio of the outer diameter of the height of the blade and the stator is between 0.15 to 0.269.

Optionally, in the rotary compressor, the outer diameter of the stator is between 132mm to 141mm.

Optionally, in the rotary compressor, the outer diameter of the stator be 132.3mm, 135.0mm or 140.1mm。

Optionally, in the rotary compressor, the outer diameter of the eccentricity of the crankshaft and the stator Ratio is between 0.029 to 0.047.

Optionally, in the rotary compressor, the outer diameter of the eccentricity of the crankshaft and the stator Ratio is 0.029,0.035 or 0.042.

Optionally, in the rotary compressor, the ratio of the outer diameter of the height of the blade and the stator Value is between 0.19 to 0.263.

Optionally, in the rotary compressor, the ratio of the outer diameter of the height of the blade and the stator Value is 0.19,0.227 or 0.25.

Optionally, in the rotary compressor, the volume of the stator is in 110cm³To 150cm³Between.

Optionally, in the rotary compressor, there are three footing, three bottoms for the rotary compressor tool Foot interval is uniform.

In the rotary compressor provided by the utility model, by the volume and outer diameter, crankshaft that control stator The ratio of the outer diameter of the height and stator of the ratio and blade of the outer diameter of eccentricity and the stator, so that The rotary compressor can keep its refrigerating capacity while reducing size and weight, to realize wanting for miniaturization It asks.

Detailed description of the invention

The technical solution of the utility model is described in detail below in conjunction with the drawings and specific embodiments, so that this reality It is become apparent with novel characteristics and advantages.

Fig. 1 is the sectional view of the rotary compressor of the utility model embodiment；

Fig. 2 be originally be the utility model embodiment crankshaft structural schematic diagram；

Fig. 3 is the structural schematic diagram of the eccentric part of the crankshaft of the utility model embodiment；

Fig. 4 is what the electric efficiency of the rotary compressor of the utility model embodiment was changed with the volume of stator Relational graph；

Fig. 5 be the rotary compressor of the utility model embodiment the coefficient of performance with blade height and stator it is outer The relational graph that the ratio of diameter size is changed；

Fig. 6 is the coefficient of performance of the rotary compressor of the utility model embodiment with the eccentricity and stator of crankshaft The relational graph that the ratio of outer diameter is changed.

Specific embodiment

To the embodiments of the present invention be provided with detailed description below.Although the utility model will be in conjunction with some specific Embodiment is illustrated and illustrates, but should be noted that the utility model is not merely confined to these embodiments. On the contrary, to modification or equivalent replacement that the utility model carries out, the scope of the claims that should all cover in the utility model is worked as In.

In addition, in order to better illustrate the utility model, given in specific embodiment below numerous specific Details.It will be understood by those skilled in the art that without these details, the utility model equally be can be implemented.In other In example, known structure and component are not described in detail, in order to highlight the purport of the utility model.

Referring to FIG. 1, its sectional view for the rotary compressor of the utility model embodiment.As shown in Figure 1, the rotation Rotary compressor 100 includes: electric machine assembly 10, compression assembly 20 and crankshaft 30；The electric machine assembly 10 includes stator 11 and turns Son 12, the rotor 12 is rotatablely arranged in the stator 11；The compression assembly 20 includes the first cylinder 21 and second Piston and blade are provided in cylinder 22, first cylinder 21 and the second cylinder 22；One end of the crankshaft 30 and institute The rotor 12 for stating electric machine assembly 10 connects, and the other end of the crankshaft 30 protrudes into first cylinder 21 and the second cylinder 22 simultaneously It is connect with the piston；Wherein, the discharge capacity of the rotary compressor 100 is between 50.0cc~59.0cc, the stator 11 Volume in 110cm³To 160cm³Between, the outer diameter of the stator 11 is between 130mm to 145mm.

Specifically, the rotary compressor 100 includes electric machine assembly 10, compression assembly 20, crankshaft 30, shell 4, upper casing Lid 5, lower cover 6, liquid storage device assembly 7, air inlet pipe 8 and exhaust pipe 9.Wherein, the shell 4 is cylinder, the upper shell cover 1 It is individually fixed in the upper and lower ends of the shell 4 with lower cover 6, exhaust pipe 9, the liquid storage device are provided on the upper shell cover 1 Component 7 is set to the outside of the shell 4 and is connected with the shell 4, is provided with air inlet pipe 8 in the liquid storage device assembly 7. The electric machine assembly 10, compression assembly 20 and crankshaft 30 are placed in the inside of the shell 4.

Wherein, the electric machine assembly 10 includes stator 11 and rotor 12, and the inner wall of the stator 11 and the shell 4 is solid Fixed, the rotor 12 is rotatablely arranged in the stator 11.The crankshaft 30 is connect with the rotor 12, and at described turn It is rotated under the drive of son 12.

The calculation formula of the volume V of the stator 11 are as follows:

Wherein, D1 is the outer diameter of the stator 11, and D2 is the internal diameter of the stator 11, and H is the stator 11 Height.

The compression assembly 20 using double cylinder engines, two cylinders are setting up and down and two cylinders in be provided with piston And blade.As shown in Figure 1, the compression assembly 20 includes the first cylinder 21 and the second cylinder 22, first cylinder 21 and the It is provided between two cylinders 22 in first cylinder 21 described in intermediate bulkhead 23 and is provided with first piston (identify and omit in figure), institute It states and is provided in the second cylinder 22 second piston (identify and omit in figure), the inner wall of the first piston and the first cylinder 21, with And the second piston and the inner wall of the second cylinder 22 have been respectively formed a crescent-shaped space, two end seals of the crescent-shaped space It closes, constitutes the working chamber of compressor, in the blade groove (identify and omit in figure) of first cylinder 21 and the second cylinder 22 point It is not provided with the first blade and the second blade (identify and omit in figure).

Wherein, the appearance face contact of one end of first blade and the first piston, first blade it is another End is contacted by spring with the inner wall of first cylinder 21, and first blade is by first cylinder 21 and first piston group At crescent-shaped space be divided into a suction chamber and a compression chamber, one end of second blade and the appearance of the second piston The other end of face contact, second blade is contacted by spring with the inner wall of second cylinder 22, and second blade will The crescent-shaped space of second cylinder 22 and second piston composition is divided into a suction chamber and a compression chamber.

In the present embodiment, the shape and size of the first piston and second piston are all the same, first blade and The shape and size of two blades are all the same.Wherein, the height of first blade and the second blade is h.

Preferably, first cylinder 21 is identical as discharge capacity (i.e. the delivery space) of the second cylinder 22.In this way, the rotation The work of formula compressor 100 is more stable.

Incorporated by reference to referring to figs. 1 to Fig. 3, the crankshaft 30 is axially extending along the shell 4, and the crankshaft 30 includes length Axis 31, short axle 32 and the eccentric part 33 being set between the long axis 31 and short axle 32, the long axis 31 are used for and the electricity The rotors 12 of thermomechanical components 10 connects, and the eccentric part 33 protrudes into first cylinder 21, in the second cylinder 22, first cylinder The second piston in first piston and second cylinder 22 in 21 is sheathed on the eccentric part 33 of the crankshaft 30 respectively.Its In, the long axis 31 is overlapped with the central axis of short axle 32, which is defined as the central axis of the crankshaft 30, described The central axis of crankshaft 30 is overlapped with the central axis of first cylinder 21 and the second cylinder 22, the center of the eccentric part 33 The distance between the central axis of axis and the crankshaft 30 is defined as the eccentric amount e of the crankshaft 30.

When the electric machine assembly 10 is powered, rotor 12 is rotated relative to stator 11, and then drives the crankshaft 30 will be electric The rotary force of thermomechanical components 10 passes to the first piston and second piston, and the first piston is with second piston respectively described It is eccentrically rotated movement in first cylinder 21 and two cylinders 22, so that the compression chamber of first cylinder 21 and the second cylinder 22 Volume constantly reduce, the volume of suction chamber is continuously increased, to realize continuous air-breathing compression process.

In the present embodiment, the rotary compressor 100 is constant speed compressor (having fixed running speed and power), The discharge capacity of the constant speed compressor is between 50.0cc~59.0cc, and the refrigerant used is R410A.

It is well known that the coefficient of performance of compressor is mainly related with pump housing efficiency and electric efficiency, pump housing efficiency and motor Efficiency is higher, then the coefficient of performance of compressor is higher.Conversely, pump housing efficiency and electric efficiency are lower, then performance demands of compressor Number is lower.

For the compressor of a fixed displacement, required output power be it is certain, the volume of stator is excessive to be will lead to Its output power is rich, causes waste of material, and the volume of stator is too small, will cause that motor feels hot is big, and electric efficiency is low, It is unable to satisfy design requirement.Therefore, powerful compressor generally uses large shell caliber to design, and low power compressor generally uses Small shell diameter design.However, the problem excessive using the generally existing volume and weight of compressor that large shell caliber designs.And compressor Volume and weight is bigger, it is meant that manufacturing cost is higher.

Applicant is by for many years the study found that work as one timing of output power of motor, the volume base of electric efficiency and stator It is positive relationship in sheet, i.e. the volume of stator is bigger, and electric efficiency is higher, but when the volume of stator reaches certain value, electricity The increase of engine efficiency can tend to slowly, if desired improve identical electric efficiency, and the volume of stator needs exponentially to increase.In order to The coefficient of performance and weight for guaranteeing compressor are in preferred range, need to control the volume of stator.

Experiments verify that for discharge capacity in 50.0cc~59.0cc, for refrigerant used is the constant speed compressor of R410A, The volume of stator is less than 110cm³When, the decline of electric efficiency clearly, is unable to satisfy design requirement, and the volume of stator is big In 160cm³When, electric efficiency tends towards stability, if continuing the volume of increase stator, the promotion of electric efficiency is very small, but compresses The weight of machine can steeply rise.

In the present embodiment, the volume V of the stator 11 is in 110cm³To 160cm³Between.Further, the stator 11 Volume V is in 110cm³To 150cm³Between.For example, the volume V of the stator 11 is 117.5cm³、143.5cm³Or 150cm³。

Referring to FIG. 4, it is the electric efficiency of the rotary compressor of the utility model embodiment with the volume of stator The relational graph being changed.As shown in figure 4, horizontal axis is the volume V of stator, the longitudinal axis is the electric efficiency E of rotary compressor, with The volume V of stator is as parameter and is allowed to variation it can be found that electric efficiency E rises with the increase of the volume V of stator, calmly The volume V of son is bigger, and electric efficiency E rising is slower, when the volume V of stator is in 110cm³To 160cm³Between, electric efficiency E In than more preferably range, when the volume V of stator is in 110cm³To 150cm³Between, electric efficiency E is in preferred model It encloses.

As shown in figure 4, when the volume V of stator is 117.5cm³When, electric efficiency E is lower, but the weight of compressor at this time Also relatively lighter；When the volume V of stator is 143.5cm³When, electric efficiency E is in a median, the electric efficiency E of compressor The level of a centre is in weight；When the volume V of stator is 150cm³When, electric efficiency E higher, but compressor at this time Weight also than heavier.

Further, it is found by the applicant that the outer diameter D1 of stator not only influences the volume V of stator, it also will affect pump housing pressure The size of shrinking structure, and then influence the weight of compressor.Common, the outer diameter D1 of stator is bigger, and pump body compression structure is just Bigger, the weight of compressor is heavier.Conversely, the outer diameter D1 of stator is smaller, pump body compression structure is with regard to smaller, the weight of compressor It measures lighter.

Applicant will affect the electric efficiency and weight of compressor in view of the outer diameter of stator, therefore in the body of stator Under the premise of product V is constant, the outer diameter D1 of the stator 11 is controlled.

In the present embodiment, the outer diameter D1 of the stator 11 is between 130mm to 145mm.Preferably, the stator Outer diameter D1 is between 132mm to 141mm.For example, the outer diameter D1 of the stator 11 be 132.3mm, 135.0mm or 140.1mm。

Experiments verify that: when the outer diameter D1 of the stator 11 is between 130mm to 145mm, the performance demands of compressor Number COP higher, while the weight W of compressor is lower；When the outer diameter D1 of stator is greater than 145mm, weight W starts sharply to increase Greatly, and coefficient of performance rise it is unobvious；When the outer diameter D1 of stator is less than 130mm, coefficient of performance is rapid Decline, is unable to satisfy displacement requirements (between 50.0cc~59.0cc).

In short, can not when the outer diameter D1 of stator is greater than the outer diameter D1 of 145mm or stator less than 130mm Meet the requirement of high-power small shell diameter simultaneously.It, could simultaneously when the outer diameter D1 of stator is less than 145mm and is greater than 130mm Meet the requirement of high-power small shell diameter.In particular, when the outer diameter D1 of stator is between 132mm to 141mm, compressor The coefficient of performance and weight be in preferable section.

In addition, the outer diameter D1 of stator also will affect the pump housing efficiency of compressor.The pump housing efficiency of compressor mainly by The volumetric efficiency and mechanical efficiency of the pump housing determine.Wherein, mainly friction loss caused by by friction pair is influenced mechanical efficiency, is wrapped It includes between outer surface of piston and blade tip, between piston interior surface and crankshaft outer surface and between blade side and blade groove Friction loss.The outer diameter D1 of stator is bigger, and pump body compression structure is bigger, correspondingly, the contact area of friction pair is just It is bigger, therefore leakage is fewer, volumetric efficiency is higher, but the secondary contact area that rubs simultaneously increases, and friction loss can be increased, to drop Low mechanical efficiency；Vice versa.

So the utility model, which passes through, rationally designs h/D1, e/D1 ratio, in the base that small shell diameter mechanical friction loss reduces Further reduce mechanical friction loss on plinth, improve mechanical efficiency, thus when making up small shell diameter volumetric efficiency deficiency.Such as This, even if stator outer diameter reduces, the pump housing efficiency of compressor can also reach level identical with big outer diameter, the property of compressor entirety Energy coefficient is not in biggish fluctuation.When the ratio (h/D1) and song of the outer diameter D1 of the height h and stator 11 of blade When the ratio (e/D1) of the outer diameter D1 of the eccentric amount e and stator 11 of axis is excessive, outer surface of piston and slide plate end stress are very Greatly, cause the friction lubricating effect poor simultaneously because slide plate is excessively high, and then increase friction loss.When blade height h with Ratio (the e/ of the outer diameter D1 of the eccentric amount e and stator 11 of the ratio (h/D1) and crankshaft of the outer diameter D1 of stator 11 D1 when) too small, although friction secondary stress and contact area can be reduced, friction loss is reduced, bring is piston therewith Thickness increases, cylinder bore diameter increases, and is unfavorable for the promotion of volumetric efficiency.

Base this, applicant rationally controls h/D1 and e/D1 respectively, to effectively reduce friction loss, improves mechanical effect Rate, to make up the deficiency of volumetric efficiency.In this way, even if the outer diameter D1 of stator is contracted to 130mm~145mm, compressor Pump housing efficiency can also reach original level (i.e. the level that does not reduce of outer diameter, such as 150mm~165mm), thus Ensure that the coefficient of performance of compressor is able to maintain that previous level.

In the present embodiment, the ratio (h/D1) of the outer diameter D1 of the height h and stator 11 of blade is 0.15 to 0.269 Between, the ratio (e/D1) of the outer diameter D1 of the eccentric amount e and stator 11 of crankshaft 30 is between 0.023 to 0.051.

Further, the ratio (h/D1) of the outer diameter D1 of the height h and stator 11 of blade 0.19 to 0.263 it Between, the ratio (e/D1) of the outer diameter D1 of the eccentric amount e and stator 11 of crankshaft 30 is between 0.029 to 0.047.For example, leaf The ratio (h/D1) of the outer diameter D1 of the height h and stator 11 of piece is 0.19,0.227 or 0.25, the eccentric amount e of crankshaft 30 Ratio (e/D1) with the outer diameter D1 of stator 11 is 0.029,0.035 or 0.042.

Incorporated by reference to reference Fig. 5 and Fig. 6, Fig. 5 be the rotary compressor of the utility model embodiment the coefficient of performance with The relational graph that the ratio of the outer diameter of the height and stator of blade is changed, Fig. 6 are the rotation of the utility model embodiment The relational graph that the coefficient of performance of formula compressor is changed with the ratio of the eccentricity of crankshaft and the outer diameter of stator.Such as figure Shown in 5 and Fig. 6, the ratio (h/D1) of the outer diameter D1 of the height h of blade and the stator 11 and the eccentric amount e of crankshaft With the coefficient of performance of the ratio (e/D1) of the outer diameter D1 of the stator 11 and compressor substantially parabolically trend, when 0.15 < h/D1 < 0.269 and when 0.023 < e/D1 < 0.051, the coefficient of performance of compressor is in optimum range, when h/D1 is greater than When 0.269 or e/D1 is greater than 0.047, the coefficient of performance of compressor is decreased obviously.

It should be noted that the coefficient of performance of rotary compressor was codetermined by h/D1 and e/D1, Fig. 5 and Fig. 6's Coefficient of performance curve is same curve.When e/D1, which is greater than 0.047 or h/D1, is greater than 0.269, friction loss is all bigger, Lead to the reduced performance of compressor.As 0.15 < h/D1 < 0.269 and 0.023 < e/D1 < 0.051, friction loss is compared It is small, therefore the performance of compressor is relatively good.

It should be noted that the modular construction involved in Compressor Technology field is numerous and structural parameters are complicated, not In the case where carrying out many experiments, the feasibility of unpredictable technical solution also fail to predict the technical effect of technical solution. The selection of technical parameter is most important, and the minor alteration of any parameter may all bring entirely different technical effect, optimizes Technical parameter all need just to can determine that by a large amount of exploitative experiment, and can not be by simply predicting to obtain.

In the present embodiment, the rotary compressor 100 is designed using small shell diameter, therefore can effectively meet compression Machine requirement small in size, light-weight.The rotary compressor 100 is compared and can be sent out with traditional constant speed compressor Existing, it is 1 that the rotary compressor 100 is identical as the refrigerating capacity of traditional constant speed compressor；The rotary compressor 100 is essentially identical with the COP index of traditional constant speed compressor, is 0.98 and 1 respectively；But the rotary compressor 100 Weight decline it is obvious, the weight of the rotary compressor 100 is about the 70% of traditional constant speed compressor.Specifically see under Table:

As it can be seen that the refrigerating capacity and COP index of the rotary compressor 100 and traditional 5HP constant speed compressor are basic It is identical.Compared with traditional 5HP constant speed compressor, the volume of the rotary compressor 100 is smaller, and weight is lighter.Institute as a result, The cold heavy ratio for stating rotary compressor 100 is significantly enhanced.

It is cold heavy than being crucial one of performance indicator for compressor.It is described cold heavy than referring to the specified of compressor The ratio of refrigerating capacity and its weight.During studying and manufacturing compressor, need to improve refrigerating capacity to the maximum extent, together When reduce the size and weight of compressor to the maximum extent, the competitiveness of product could be improved, obtain best economic benefit.

Simultaneously as the lighter in weight of the rotary compressor 100, therefore the design of three footing, three bottoms can be used The design of foot is enough to support entire compressor weight.In the present embodiment, the rotary compressor 100 includes three footing (figure In be not shown), three footing intervals uniformly and be fixedly connected by welding manner with the bottom of lower cover 6.

In summary, volume and outer diameter, crankshaft that the rotary compressor of the utility model passes through control stator The ratio of the outer diameter of the height and stator of the ratio and blade of the outer diameter of eccentricity and the stator, so that The rotary compressor can keep its refrigerating capacity while reducing size and weight, to realize wanting for miniaturization It asks.

The above content is combine specific preferred embodiment to made by the application further description, and it cannot be said that The specific implementation of the application is only limited to these instructions.For those of ordinary skill in the art to which this application belongs, In Under the premise of not departing from the application design, a number of simple deductions or replacements can also be made, all shall be regarded as belonging to the application's Protection scope.

Claims

1. a kind of rotary compressor characterized by comprising electric machine assembly, compression assembly and crankshaft；

The compression assembly includes the first cylinder and the second cylinder, be provided in first cylinder and the second cylinder piston and Blade；

One end of the crankshaft is connect with the rotor of the electric machine assembly, the other end of the crankshaft protrude into first cylinder and It is connect in second cylinder and with the piston；

Wherein, the discharge capacity of the rotary compressor is between 50.0cc~59.0cc, and the volume of the stator is in 110cm³It arrives 160cm³Between, the outer diameter of the stator is between 130mm to 145mm.

2. rotary compressor as described in claim 1, which is characterized in that the eccentricity of the crankshaft is outer with the stator The ratio of diameter size is between 0.023 to 0.051, and the ratio of the outer diameter of the height of the blade and the stator is 0.15 To between 0.269.

3. rotary compressor as claimed in claim 1 or 2, which is characterized in that the outer diameter of the stator is arrived in 132mm Between 141mm.

4. rotary compressor as claimed in claim 3, which is characterized in that the outer diameter of the stator be 132.3mm, 135.0mm or 140.1mm.

5. rotary compressor as claimed in claim 2, which is characterized in that the eccentricity of the crankshaft is outer with the stator The ratio of diameter size is between 0.029 to 0.047.

6. rotary compressor as claimed in claim 5, which is characterized in that the eccentricity of the crankshaft is outer with the stator The ratio of diameter size is 0.029,0.035 or 0.042.

7. rotary compressor as claimed in claim 2, which is characterized in that the outer diameter of the height of the blade and the stator The ratio of size is between 0.19 to 0.263.

8. rotary compressor as claimed in claim 7, which is characterized in that the outer diameter of the height of the blade and the stator The ratio of size is 0.19,0.227 or 0.25.

9. rotary compressor as claimed in claim 1 or 2, which is characterized in that the volume of the stator is in 110cm³It arrives 150cm³Between.

10. rotary compressor as described in claim 1, which is characterized in that the rotary compressor has there are three footing, Three footing intervals are uniform.