CN105840508A - Rotary compressor and refrigeration circulation device comprising same - Google Patents
Rotary compressor and refrigeration circulation device comprising same Download PDFInfo
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- CN105840508A CN105840508A CN201610329906.7A CN201610329906A CN105840508A CN 105840508 A CN105840508 A CN 105840508A CN 201610329906 A CN201610329906 A CN 201610329906A CN 105840508 A CN105840508 A CN 105840508A
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- slide plate
- rotary compressor
- compressor
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
Abstract
The invention discloses a rotary compressor and a refrigeration circulation device comprising same. The rotary compressor adopts an R290 refrigerant and comprises a shell, N cylinders and a crankshaft, wherein the shell comprises a main shell, an upper shell and a lower shell; a cylinder cavity and a sliding sheet groove are formed in each cylinder; a piston capable of eccentrically rotating is arranged inside each cylinder cavity; the total displacement of the rotary compressor is Q sum (cm<3>); Q sum is NQ; Q is displacement of each cylinder; the inner diameter of the main shell is D(cm); the total displacement Q sum and the inner diameter D of the main shell meet the following relation formula: Q sum is greater than or equal to 2.1 and less than or equal to 4; the displacement Q of each cylinder is phi(d12/d22)*h/4; d1 is the inner diameter of the corresponding cylinder; d2 is the outer diameter of the piston of the corresponding cylinder; h is the height of the corresponding cylinder. Through the rotary compressor according to the embodiment of the invention, the cost performance of the rotary compressor adopting the R290 refrigerant can be improved.
Description
Technical field
The present invention relates to refrigerating field, especially relate to a kind of rotary compressor and there is its freezing cycle device.
Background technology
Rotary compressor generally comprises the compression mechanism and motor being located in housing, and compression mechanism includes cylinder, base bearing and
Supplementary bearing is separately positioned on the both sides of cylinder, bent axle axially through supplementary bearing, cylinder and base bearing, bent axle include main shaft,
Eccentric part, countershaft three part, piston bush is located on the eccentric part of bent axle. motor includes stator and rotor, the main shaft of bent axle with turn
Son connects together, and rotor banding dynamic crankshaft rotates, and the eccentric part of bent axle drives piston to roll, slide plate be connected on outside piston and
Move back and forth in cylinder vane slot under the promotion of piston.
Rotary compressor can be with the coolant such as R410A, R290, due to the existence of coolant property difference, uses different cold
The performance of the rotary compressor of matchmaker has bigger difference, and what the compressor arrangement of reference employing R410A coolant designed makes
Cost performance with the compressor of R290 coolant is relatively low.
Summary of the invention
It is contemplated that one of technical problem solved the most to a certain extent in correlation technique.
To this end, the present invention proposes a kind of rotary compressor, the sexual valence of the rotary compressor using R290 coolant can be improved
Ratio.
The present invention also proposes a kind of freezing cycle device with above-mentioned rotary compressor.
Rotary compressor according to embodiments of the present invention, described rotary compressor uses R290 coolant, described rotary pressure
Contracting machine includes: housing, and described housing includes that main casing, upper shell and lower house, described upper shell and described lower house are respectively
It is located at the opening part at the two ends up and down of described main casing；N number of cylinder, each described cylinder is located in described housing, Mei Gesuo
State cylinder and be provided with cylinder chamber and vane slot, in each described cylinder chamber, be provided with the piston of eccentric rotary, each described vane slot
Inside being provided with reciprocating slide plate, the tip of each described slide plate contacts with the periphery wall of corresponding described piston, wherein N >=1；
Bent axle, described bent axle runs through each described cylinder, and described bent axle includes main shaft and at least one bias being located on described main shaft
Portion, each described piston jacket is on corresponding described eccentric part；The total displacement of wherein said rotary compressor is QAlways(cm3),
QAlways=NQ, wherein Q is the discharge capacity of each described cylinder, and the internal diameter of described main casing is D (cm), described total displacement QAlwaysWith master
Following relational expression: 2.1≤Q is met between the internal diameter D of housingAlways/ D≤4, the discharge capacity Q=π (d of each described cylinder1 2-d2 2) * h/4,
Wherein d1For the internal diameter of corresponding cylinder, d2For being located at the external diameter of the piston in corresponding cylinder, h is the height of respective cylinder.
Rotary compressor according to embodiments of the present invention, by making 2.1≤QAlways/ D≤4, use R290 such that it is able to improve
The cost performance of the rotary compressor of coolant.
In some embodiments of the invention, the tip of each described slide plate is only against on the periphery wall of described piston, Mei Gesuo
State the slide plate of slide plate and stretch out the span of rate m and be: 0.4 ＜ m ＜ 0.6, wherein said slide plate stretches out rate m=(d1-d2)/L,
Wherein d1For corresponding cylinder bore diameter, d2For corresponding piston external diameter, L is corresponding slide plate length.
In some embodiments of the invention, described upper shell and described main casing are for being welded to connect, and described lower house is with described
Main casing is for being welded to connect.
Freezing cycle device according to embodiments of the present invention, including rotary compressor according to the above embodiment of the present invention.
Freezing cycle device according to embodiments of the present invention, by using rotary compressor according to the above embodiment of the present invention,
Thus improve the cost performance of the compressor using R290 coolant.
Accompanying drawing explanation
Fig. 1 is the profile of the rotary compressor according to the embodiment of the present invention；
Fig. 2 is the top view of the compression mechanism of the rotary compressor according to the embodiment of the present invention；
Fig. 3 is according to the piston in the rotary compressor of the embodiment of the present invention and the fiting relation figure between corresponding slide plate；
Fig. 4 is electric efficiency ηmoGraph of relation with motor outer diameter D 1 change；
Fig. 5 is compressor mechanical efficiency ηmGraph of relation with the change of slide plate overall length L；
Fig. 6 is the graph of relation that motor cost changes with motor outer diameter D 1；
Fig. 7 is cost and the efficiency of compressor, with QAlwaysThe graph of relation of/D change；
Fig. 8 is that compressor cost performance η/C is with QAlwaysThe graph of relation of/D change；
Fig. 9 is electric efficiency η of R290 cold medium compressor and R410A cold medium compressormoRelation with motor outer diameter D 1 change
Curve；
Figure 10 is mechanical efficiency η of R290 cold medium compressor and R410A cold medium compressormRelation with the change of slide plate overall length L
Curve；
Figure 11 is that R290 cold medium compressor cost performance η/C with R410A cold medium compressor is with QAlwaysThe relation curve of/D change；
Figure 12 is that R290 cold medium compressor slide plate side frictional power loss stretches out the relation curve of rate m change with slide plate.
Reference:
Rotary compressor 100,
Upper shell 10, main casing 11, lower house 12,
Cylinder 2, cylinder chamber 20, compression chamber 20a, suction muffler 20b, vane slot 21,
Piston 3, slide plate 4,
Bent axle 5, main shaft 50, eccentric part 51,
Base bearing 6, supplementary bearing 7,
Motor 8, stator 80, rotor 81.
Detailed description of the invention
Embodiments of the invention are described below in detail, and the example of described embodiment is shown in the drawings.Below with reference to accompanying drawing
The embodiment described is exemplary, it is intended to is used for explaining the present invention, and is not considered as limiting the invention.
In describing the invention, it is to be understood that term " " center ", " longitudinally ", " laterally ", " length ", " width ",
" thickness ", " on ", D score, "front", "rear", "left", "right", " vertically ", " level ", " top ", " end " " interior ",
" outward ", " clockwise ", " counterclockwise ", " axially ", " radially ", " circumferential " etc. instruction orientation or position relationship be based on
Orientation shown in the drawings or position relationship, be for only for ease of the description present invention and simplify description rather than instruction or hint institute
The device that refers to or element must have specific orientation, with specific azimuth configuration and operation, therefore it is not intended that to this
Bright restriction.
Additionally, term " first ", " second " are only used for describing purpose, and it is not intended that instruction or hint relative importance
Or the implicit quantity indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can be expressed
Or implicitly include at least one this feature.In describing the invention, " multiple " are meant that at least two, such as two
Individual, three etc., unless otherwise expressly limited specifically.
In the present invention, unless otherwise clearly defined and limited, term " install ", " being connected ", " connection ", " fixing "
Should be interpreted broadly Deng term, connect for example, it may be fixing, it is also possible to be to removably connect, or integral；Can be
Be mechanically connected, it is also possible to be electrical connection or each other can communication；Can be to be joined directly together, it is also possible to by the indirect phase of intermediary
Even, can be connection or the interaction relationship of two elements of two element internals, unless otherwise clear and definite restriction.For
For those of ordinary skill in the art, above-mentioned term concrete meaning in the present invention can be understood as the case may be.
Rotary compressor 100 according to embodiments of the present invention, this rotary compressor is described in detail below with reference to Fig. 1-Figure 12
100 can be that single cylinder rotary compressor can also be for multi-cylinder rotary compressor, and this rotary compressor 100 uses R290
Coolant.Wherein for the ease of describing, in the following description rotary compressor 100 is sketched as compressor.
As depicted in figs. 1 and 2, rotary compressor 100 according to embodiments of the present invention includes: housing, compression mechanism and
Motor, compression mechanism includes N number of cylinder 2 and bent axle 5, wherein N >=1.Compression mechanism and motor are respectively provided in housing,
Motor 8 includes stator 80 and rotor 81, and stator 80 is fixed on the inwall of housing, and specifically, stator 80 can pass through
Interference fit, weld or the mode such as riveting is fixed on housing.It is understood that compression mechanism also includes base bearing 6
With supplementary bearing 7 element such as grade.Will also be appreciated that the operation principle of rotary compressor 100 for prior art, here
It is not described in detail.
Housing includes that main casing 11, upper shell 10 and lower house 12, upper shell 10 and lower house 12 are respectively provided at main casing
The opening part at the two ends up and down of 11, say, that main casing 11 is formed as the structure of the hollow of upper and lower open at both ends, on
Housing 10 is located at the upper end upper end open with closing main casing 11 of main casing 11, and lower house 12 is located at main casing 11 times
Hold to close the lower ending opening of main casing 11.Alternatively, upper shell 10 and main casing 11 for being welded to connect, lower house 12
With main casing 11 for being welded to connect.
Each cylinder 2 is located in housing, and each cylinder 2 is provided with cylinder chamber 20 and vane slot 21, in each cylinder chamber 20
It is provided with the piston 3 of eccentric rotary, in each vane slot 21, is provided with reciprocating slide plate 4, the tip of each slide plate 4 and phase
The periphery wall contact of the piston 3 answered.Specifically, the piston 3 of each cylinder 2 correspondence coordinates with slide plate 4 with by corresponding gas
Cylinder chamber 20 is separated into suction muffler 20b and compression chamber 20a.It is understood that when cylinder 2 is multiple, adjacent cylinder
The both sides that median septum, base bearing 6 and supplementary bearing 7 are respectively provided at the air cylinder group of multiple cylinder 2 composition it are provided with between 2.Work as gas
When cylinder 2 is one, base bearing 6 and supplementary bearing 7 are located at the both sides of cylinder 2.
Bent axle 5 runs through each cylinder 2, and bent axle 5 includes main shaft 50 and at least one eccentric part 51 being located on main shaft 50,
Being enclosed within outside each piston 3 on corresponding eccentric part 51, main shaft 50 is fixed on rotor 81, and motor 8 runs to drive bent axle
5 rotate thus drive each piston 3 eccentric rotary in corresponding cylinder chamber 20.
Wherein the total displacement of rotary compressor 100 is QAlways(cm3), QAlways=NQ, wherein Q is the discharge capacity of each cylinder 2,
The internal diameter of main casing 11 is D (cm), the discharge capacity Q=π (d of each cylinder 21 2-d2 2) * h/4, the slide plate of slide plate 4 stretches out rate
M=(d1-d2)/L, wherein d1For the internal diameter of corresponding cylinder 2, d2For being located at the external diameter of the piston 3 in corresponding cylinder 2, h
For the height of respective cylinder 2, L is the length of corresponding slide plate 4.
Specifically, the Energy Efficiency Ratio computing formula of compressor is as follows: η=ηvηiηmηmoηad, wherein, η is compressor Energy Efficiency Ratio,
ηvFor compressor volumetric efficiency, ηiFor compressor indicated efficiency, ηmFor compressor mechanical efficiency, ηmoFor electric efficiency.
When the discharge capacity of compressor determines, main casing 11 internal diameter D increases, then motor 8 outer diameter D 1 increases therewith, and motor 8 is imitated
Rate ηmoCan promote accordingly, as shown in Figure 4, motor 8 efficiency etamoLifting and motor 8 outer diameter D 1 increasing the most linearly
Relation, motor 8 outer diameter D 1 is the biggest, motor 8 efficiency etamoThe slope strengthened with motor 8 outer diameter D 1 reduces.
It addition, compression mechanism outer diameter D 2 strengthens the most accordingly, slide plate 4 can lengthen to promote compressor efficiency accordingly.Slide plate 4 is total
The overall length of the long vane slot 21 being limited on cylinder 2, as shown in Figure 2, when compressing mechanism's outer diameter D 2 and increasing, can protect
Strengthen the length of vane slot 21 on the premise of card vane slot 21 minimum wall thickness (MINI W.), thus strengthen the overall length of slide plate 4.Such as Fig. 3 institute
Showing, the tip of each slide plate 4 is only against on the periphery wall of piston 3, and slide plate 4 extend out to the part in cylinder chamber 20 by air-breathing
Chamber 20b low pressure and the differential pressure action power of compression chamber 20a high pressure, be positioned at slide plate 4 both sides of vane slot 21 by vane slot 21
Support, form lever, in the middle part of slide plate 4, be fulcrum, the one of the length of slide plate 4 extension with cylinder 2 inner circle contact position
Partly being the arm of force L1 of difference force F1, slide plate 4 afterbody is F2 with the pressure of vane slot 21 contact position, and the arm of force is L2,
Point pressure F3, according to equalising torque and dynamic balance, meets relationship below:
F1*L1=F2*L2
F3=F1+F2
If slide plate 4 overall length is L, then L=2*L1+L2, therefore can derive:
F2=F1*L1/ (L-2*L1)
It follows that in the case of slide plate 4 extension length 2*L1 and suffered difference force F1 are constant, strengthen slide plate 4
Overall length L can reduce the pressure F2 of slide plate 4 afterbody and vane slot 21 contact position, and pressure F3 at fulcrum, and this is subject at two
After power reduces, slide plate 4 move back and forth vane slot 21 in suffered by frictional force i.e. reduce, the frictional work of compressor operation consumes
Losing and reduce, compressor horsepower reduces, compressor mechanical efficiency ηmImproving, Energy Efficiency Ratio η increases.
As it is shown in figure 5, compressor mechanical efficiency ηmLifting and slide plate 4 length strengthen the most linear, slide plate 4 is more
Long, compressor mechanical efficiency ηmThe slope increased with slide plate 4 overall length L reduces.
It is understood that the cost of motor 8 is relevant to the volume of motor 8, the cost of motor 8 is with the outer diameter D 1 of motor 8
Strengthening and increase, as shown in Figure 6, the outer diameter D 1 of motor 8 is the biggest, and the cost of motor 8 increases with the outer diameter D 1 of motor 8
Slope the biggest.
In sum, the cost of compressor and efficiency and discharge capacity Q of compressorAlways(cm3) and the internal diameter D (cm) of main casing 11
Between ratio QAlwaysRelation curve between/D is as shown in Figure 7.
Energy Efficiency Ratio η of compressor and the ratio of cost C, can be considered the cost performance of compressor, cost performance η/C and QAlways/ D it
Between relation curve as shown in Figure 8, cost performance η/C is with QAlways/ D increases first to increase and subtracts afterwards, there is flex point, i.e. there is optimum
QAlways/ D makes the cost performance of compressor the highest.
For using the compressor of R410A coolant, Q corresponding during cost performance optimumAlways/ D is about 1.8, uses R410A at present
The Q of the compressor of coolantAlways/ D is between 1.4～2.0 mostly, so that compressor cost performance is more excellent.
For using the compressor of environmental protection new cooling media R290, the employing R410A coolant of same displacement is still used for reference in current design
Compressor.But R290 Yu R410A coolant property difference is relatively big, key property difference such as following table:
It should be noted that the comparison premise of above characteristic be evaporating temperature in the refrigeration residing for compressor or heating,
Delivery temperature, compressor air suction temperature are the most identical.
Existence due to above coolant property difference so that the Q when compressor cost performance of employing R290 coolant is more excellentAlways/ D takes
Value has larger difference with the compressor using R410A coolant, uses for reference the compressor arrangement design of existing employing R410A coolant
The cost performance of the compressor of employing R290 coolant out is relatively low.Need to illustrate, for the ease of describing, will use
The compressor summary of R290 coolant is R290 cold medium compressor, by cold for R410A for the compressor summary using R410A coolant
Matchmaker's compressor.
Above-mentioned coolant property difference is to Q during cost performance optimized designAlwaysThe impact of/D value is:
Little with R290 theoretical compression power during discharge capacity so that R290 cold medium compressor relatively exists with discharge capacity R410A cold medium compressor
Motor 8 efficiency phase simultaneously need to motor 8 outer diameter D 1 reduce, as it is shown in figure 9, electric efficiency η of R290 cold medium compressormo
Variation relation curve with motor outer diameter D 1 and electric efficiency η with discharge capacity R410A cold medium compressormoWith motor outer diameter D 1
The difference of variation relation curve is that the curve of R290 cold medium compressor moves to left compared with the curve entirety of R410A cold medium compressor.
R290 drain pressure and suction and discharge pressure difference are little so that slide plate 4 lateral forces reduces, rubbing when slide plate 4 moves back and forth
Wiping power loss reduces, and slide plate 4 lengthens compressor mechanical efficiency ηmLifting amplitude reduction, as shown in Figure 10, R290
Mechanical efficiency η of cold medium compressormRelation curve (in figure shown in dotted line) and R410A coolant pressure with the change of slide plate overall length L
Mechanical efficiency η of contracting machinemDifference with the relation curve (in figure shown in solid) of slide plate overall length L change is R290 coolant pressure
The curve of contracting machine moves to left compared with the curve entirety of R410A cold medium compressor.
In sum, R290 cold medium compressor efficiency and discharge capacity QAlwaysAnd the ratio Q between main casing 11 internal diameter DAlwaysThe pass of/D
Being curve, the curve entirety being equivalent to R410A cold medium compressor as shown in Figure 7 moves to left, and compressor cost and QAlways/D
Relation curve the most constant, therefore R290 cold medium compressor cost performance η/C and QAlwaysRelation curve between/D is cold compared with R410A
Matchmaker's compressor cost performance η/C and QAlwaysThe difference of the relation curve between/D as shown in figure 11, Q corresponding during cost performance optimumAlways/ D value relatively R410A is increased to 2.5 by 1.8.
Therefore, for promoting the cost performance of R290 cold medium compressor, in rotary compressor 100 according to embodiments of the present invention
Total displacement QAlwaysAnd meet following relational expression between the internal diameter D of main casing 11:
2.1≤QAlways/D≤4。
Rotary compressor 100 according to embodiments of the present invention, by making 2.1≤QAlways/ D≤4, use such that it is able to improve
The cost performance of the rotary compressor 100 of R290 coolant.
It is understood that the height reducing cylinder 2 can reduce the radial leakage between piston 3 cylindrical and cylinder 2 inner circle, and
And the area reducing cylinder 2 inwall can reduce compression mechanism external high temperature refrigerator oil to the heat transfer loss within cylinder 2,
But according to formula for displacement calculation Q=π (d1 2-d2 2)*h/4(d1For cylinder 2 internal diameter, d2For piston 3 external diameter, h is that cylinder 2 is high
Degree), on the premise of ensureing that discharge capacity Q is certain, if reducing cylinder 2 height h, then need to increase cylinder 2 internal diameter d1 or reduction
Piston 3 outside diameter d 2.
Slide plate according to slide plate 4 stretches out rate formula m=(d1-d2)/L, wherein d1For cylinder 2 internal diameter, d2For piston 3 external diameter,
In the case of main casing 11 internal diameter D is certain, compression mechanism outer diameter D 2 is also certain, for ensureing at the vane slot 21 of cylinder 2
Minimum wall thickness (MINI W.), if cylinder 2 internal diameter d1 increases, then vane slot 21 length needs to reduce, and slide plate 4 length limited is in vane slot 21
Length also needs to reduce.
To sum up, slide plate 4 is necessarily caused to stretch out the increase of rate m, by Fig. 3 and above-mentioned slide plate 4 side if cylinder 2 height reduces
Force analysis understands, and the slide plate of slide plate 4 stretches out the increase of rate m and necessarily causes slide plate 4 lateral forces to increase, and slide plate 4 is at slide plate
Side frictional power loss when moving back and forth in groove 21 strengthens, and the slide plate of slide plate 4 stretches out rate m when increasing to a certain degree,
Slide plate 4 side lubrication circumstances deteriorates, and coefficient of friction drastically strengthens, and frictional power loss sharply increases, and slide plate 4 side rubs
The slide plate of loss and slide plate 4 stretches out the relation curve of rate m as shown in figure 12.
For R290 cold medium compressor, the slide plate rate of stretching out of slide plate 4 increases to about 0.6, and slide plate 4 side lubrication circumstances is disliked
Changing, coefficient of friction drastically strengthens, and frictional power loss presents sharp increase, and the comprehensive cylinder height that reduces is to promote compressor efficiency (simultaneously
The slide plate of slide plate 4 stretches out rate m and strengthens), and control slide plate 4 side frictional power loss and do not occur drastically strengthening, at this
In some bright embodiments, the span that the slide plate of slide plate 4 stretches out rate m is defined to: 0.4 ＜ m ＜ 0.6.
Freezing cycle device according to embodiments of the present invention, including rotary compressor 100 according to the above embodiment of the present invention.
Freezing cycle device according to embodiments of the present invention, by using rotary compressor according to the above embodiment of the present invention
100, thus improve the cost performance of the compressor using R290 coolant.
In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score can
Being that the first and second features directly contact, or the first and second features are by intermediary mediate contact.And, the
One feature second feature " on ", " top " and " above " but fisrt feature directly over second feature or
Oblique upper, or it is merely representative of fisrt feature level height higher than second feature.Fisrt feature second feature " under ",
" lower section " and " below " can be fisrt feature immediately below second feature or obliquely downward, or it is special to be merely representative of first
Levy level height less than second feature.
In the description of this specification, reference term " embodiment ", " some embodiments ", " example ", " specifically show
Example " or the description of " some examples " etc. means to combine this embodiment or example describes specific features, structure, material or
Feature is contained at least one embodiment or the example of the present invention.In this manual, the schematic representation to above-mentioned term
Necessarily it is directed to identical embodiment or example.And, the specific features of description, structure, material or feature are permissible
One or more embodiment in office or example combine in an appropriate manner.Additionally, in the case of the most conflicting, ability
The feature of the different embodiments described in this specification or example and different embodiment or example can be entered by the technical staff in territory
Row combines and combination.
Although above it has been shown and described that embodiments of the invention, it is to be understood that above-described embodiment is exemplary,
Being not considered as limiting the invention, those of ordinary skill in the art within the scope of the invention can be to above-described embodiment
It is changed, revises, replaces and modification.
Claims (4)
1. a rotary compressor, it is characterised in that described rotary compressor uses R290 coolant, described rotary
Compressor includes:
Housing, described housing includes that main casing, upper shell and lower house, described upper shell and described lower house are respectively provided at institute
State the opening part at the two ends up and down of main casing；
N number of cylinder, each described cylinder is located in described housing, and each described cylinder is provided with cylinder chamber and vane slot, each
It is provided with the piston of eccentric rotary in described cylinder chamber, in each described vane slot, is provided with reciprocating slide plate, each described cunning
The tip of sheet contacts with the periphery wall of corresponding described piston, wherein N >=1；
Bent axle, described bent axle runs through each described cylinder, and described bent axle includes main shaft and at least one being located on described main shaft
Eccentric part, each described piston jacket is on corresponding described eccentric part；
The total displacement of wherein said rotary compressor is QAlways(cm3), QAlways=NQ, wherein Q is the discharge capacity of each described cylinder,
The internal diameter of described main casing is D (cm), described total displacement QAlwaysAnd meet following relational expression between the internal diameter D of main casing: 2.1
≤QAlways/ D≤4, the discharge capacity Q=π (d of each described cylinder1 2-d2 2) * h/4, wherein d1For the internal diameter of corresponding cylinder, d2For setting
The external diameter of the piston in corresponding cylinder, h is the height of respective cylinder.
Rotary compressor the most according to claim 1, it is characterised in that the tip of each described slide plate is only against institute
Stating on the periphery wall of piston, the slide plate of each described slide plate stretches out the span of rate m and is: 0.4 ＜ m ＜ 0.6, wherein said
Slide plate stretches out rate m=(d1-d2)/L, wherein d1For corresponding cylinder bore diameter, d2For corresponding piston external diameter, L is corresponding sliding
Leaf length.
Rotary compressor the most according to claim 1, it is characterised in that described upper shell and described main casing are weldering
Connecing in succession, described lower house and described main casing are for being welded to connect.
4. a freezing cycle device, it is characterised in that include according to the rotary pressure according to any one of claim 1-3
Contracting machine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610329906.7A CN105840508A (en) | 2016-05-17 | 2016-05-17 | Rotary compressor and refrigeration circulation device comprising same |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610329906.7A CN105840508A (en) | 2016-05-17 | 2016-05-17 | Rotary compressor and refrigeration circulation device comprising same |
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| CN105840508A true CN105840508A (en) | 2016-08-10 |
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| CN201610329906.7A Pending CN105840508A (en) | 2016-05-17 | 2016-05-17 | Rotary compressor and refrigeration circulation device comprising same |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111255688A (en) * | 2018-11-30 | 2020-06-09 | 上海海立电器有限公司 | Air conditioning system and variable frequency compressor thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
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