CN107061273B - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- CN107061273B CN107061273B CN201611095257.5A CN201611095257A CN107061273B CN 107061273 B CN107061273 B CN 107061273B CN 201611095257 A CN201611095257 A CN 201611095257A CN 107061273 B CN107061273 B CN 107061273B
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- rotary compressor
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- crankshaft
- piston
- eccentric part
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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
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
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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
-
- 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
- F04C2240/00—Components
- F04C2240/50—Bearings
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a kind of rotary compressors, it include: shell and compression mechanism, compression mechanism is located in shell, compression mechanism includes cylinder assembly and crankshaft, cylinder assembly includes at least one cylinder, cylinder has cylinder chamber, piston is equipped in cylinder chamber, crankshaft runs through cylinder assembly, crankshaft includes crankshaft body and at least one eccentric part for being located on crankshaft body, piston is set on eccentric part, cylinder is equipped with sliding vane groove, radial clearance between the periphery wall of piston and the internal perisporium of corresponding cylinder chamber is δ, eccentric part from the central axis of sliding vane groove along the angle that the traffic direction of rotary compressor rotates be θ when δ there is minimum value δmin, θ satisfaction: 280 °≤θ≤340 °.Rotary compressor according to the present invention, can be by smallest radial gap deltaminWhat is be arranged is smaller, reduces friction loss and improves refrigerating capacity, greatly improves the Performance And Reliability of rotary compressor.
Description
Technical field
The present invention relates to Compressor Technology fields, more particularly, to a kind of rotary compressor.
Background technique
In the related technology, compressor such as rotary compressor is as a kind of high-precision engineering goods, piston it is outer
Radial clearance between peripheral wall and the internal perisporium of cylinder chamber is most important for compressor performance and reliability.If gap setting
It is too small, due to the effect of the factors such as foozle, operating load, it may cause stuck compressor, inordinate wear or friction loss
It is excessive；If gap setting is excessive, it will be increased dramatically by the refrigerant of the leakage of radial clearance, compressor performance is caused to decline.
In addition, radial clearance setting is unreasonable, rotary compressor friction loss and coolant leakage cannot be in a better balance point,
It is unfavorable for the promotion of compressor performance.
Summary of the invention
The present invention is directed at least solve one of the technical problems existing in the prior art.For this purpose, one object of the present invention
It is to propose a kind of rotary compressor, the high reliablity and performance of the rotary compressor are high.
Rotary compressor according to the present invention, comprising: shell；Compression mechanism, the compression mechanism are located at the shell
Interior, the compression mechanism includes cylinder assembly and crankshaft, and the axial ends of the cylinder assembly is respectively equipped with base bearing and countershaft
It holds, the cylinder assembly includes at least one cylinder, and the cylinder has cylinder chamber, and piston is equipped in the cylinder chamber, described
Crankshaft runs through the cylinder assembly, and the crankshaft includes crankshaft body and at least one bias being located on the crankshaft body
Portion, the piston are set on the eccentric part, and the cylinder is equipped with sliding vane groove, by the crankshaft body edge and the crankshaft
The opposite direction of eccentric direction be adjacent to one of them in the base bearing and the supplementary bearing and by the piston along with it is described
When the contrary direction of crankshaft eccentric is adjacent to the eccentric part, the periphery wall of the piston is interior with the corresponding cylinder chamber
Radial clearance between peripheral wall is δ, and the eccentric part is from the central axis of the sliding vane groove along the fortune of the rotary compressor
The δ has minimum value δ when the angle of line direction rotation is θmin, the θ satisfaction: 280 °≤θ≤340 °.
Rotary compressor according to the present invention, by setting eccentric part from the central axis of sliding vane groove along rotary compression
When the angle, θ of the traffic direction rotation of machine is 280 °≤θ≤340 °, the periphery wall of piston and the internal perisporium of corresponding cylinder chamber it
Between radial clearance δ have minimum value δmin, efficiently reduce the wave of the radial clearance of rotary compressor in the process of running
It is dynamic, so that rotary compressor is in the process of running, when so that rotary compressor being run, between the radial direction between piston and cylinder
Gap is in compared with the figure of merit always, and then can be by smallest radial gap deltaminWhat is be arranged is smaller, reduces friction loss and improves system
Cooling capacity greatly improves the Performance And Reliability of rotary compressor.
In addition, rotary compressor according to the present invention can also have the following additional technical features:
According to some embodiments of the present invention, the θ further satisfaction: θ=310 °.
Specifically, the minimum value δ of the radial clearanceminMeet: 10 μm≤δmin≤20μm。
According to some embodiments of the present invention, the internal diameter of the cylinder is D, and the outer diameter of the piston is Dro, the piston
Internal diameter be Dri, the eccentricity of the crankshaft is e, in the base bearing and the supplementary bearing it is described one of them with the song
The internal diameter of the matching hole of shaft body cooperation is Db, the diameter of the eccentric part is Dse, the crankshaft body with the base bearing
It is D with the diameter at one of cooperation in the supplementary bearingsb, described D, Dro、Dri、e、Db、Dse、Dsb、δminMeet:
|D-Dro-2e-2δmin+0.625(Dri+Db-Dse-Dsb)|≤10μm。
Optionally, described D, Dro、Dri、e、Db、Dse、Dsb, δ min further satisfaction:
D-Dro-2e-2δmin+0.625(Dri+Db-Dse-Dsb)=0.
Optionally, the rotary compressor is single cylinder compressor.
Optionally, the rotary compressor is duplex cylinder compressor.
Optionally, the rotary compressor is constant speed compressor.
Optionally, the rotary compressor is frequency-changeable compressor.
Additional aspect and advantage of the invention will be set forth in part in the description, and will partially become from the following description
Obviously, or practice through the invention is recognized.
Detailed description of the invention
Above-mentioned and/or additional aspect of the invention and advantage will become from the description of the embodiment in conjunction with the following figures
Obviously and it is readily appreciated that, in which:
Fig. 1 is the cut-away view of the compression mechanism of rotary compressor according to an embodiment of the present invention；
Fig. 2 is the schematic diagram of the radial clearance setting of rotary compressor according to an embodiment of the present invention；
Fig. 3 is the change of rotary compressor according to an embodiment of the present invention dynamic clearance and static clearance in the process of running
Change curve graph；
Fig. 4 is the schematic diagram of the radial clearance setting of rotary compressor in the related technology；
Fig. 5 is the change curve of rotary compressor in the related technology dynamic clearance and static clearance in the process of running
Figure.
Appended drawing reference:
Compression mechanism 100,
Crankshaft body 11, eccentric part 12,
Cylinder 2, cylinder chamber 21, piston 22, sliding vane groove 23, air entry 24, exhaust outlet 25,
Base bearing 3, supplementary bearing 4.
Specific embodiment
The embodiment of the present invention is described below in detail, examples of the embodiments are shown in the accompanying drawings, wherein from beginning to end
Same or similar label indicates same or similar element or element with the same or similar functions.Below with reference to attached
The embodiment of figure description is exemplary, and for explaining only the invention, and is not considered as limiting the invention.
In the description of the present invention, it is to be understood that, term " center ", "upper", "lower", "front", "rear", " left side ",
" right side ", "vertical", "horizontal", "top", "bottom", "inner", "outside", " clockwise ", " counterclockwise ", " axial direction ", " radial direction ", " circumferential direction "
The orientation or positional relationship of equal instructions is to be based on the orientation or positional relationship shown in the drawings, be merely for convenience of the description present invention and
Simplify description, rather than the device or element of indication or suggestion meaning must have a particular orientation, with specific orientation construction
And operation, therefore be not considered as limiting the invention.In addition, term " first ", " second " are used for description purposes only, without
It can be interpreted as indication or suggestion relative importance or implicitly indicate the quantity of indicated technical characteristic.Define as a result, " the
One ", the feature of " second " can explicitly or implicitly include one or more of the features.In the description of the present invention,
Unless otherwise indicated, the meaning of " plurality " is two or more.
In the description of the present invention, it should be noted that unless otherwise clearly defined and limited, term " installation ", " phase
Even ", " connection " shall be understood in a broad sense, for example, it may be being fixedly connected, may be a detachable connection, or be integrally connected；It can
To be mechanical connection, it is also possible to be electrically connected；It can be directly connected, can also can be indirectly connected through an intermediary
Connection inside two elements.For the ordinary skill in the art, above-mentioned term can be understood at this with concrete condition
Concrete meaning in invention.
In the present invention unless specifically defined or limited otherwise, fisrt feature second feature "upper" or "lower"
It may include that the first and second features directly contact, also may include that the first and second features are not direct contacts but pass through it
Between other characterisation contact.Moreover, fisrt feature includes the first spy above the second feature " above ", " above " and " above "
Sign is right above second feature and oblique upper, or is merely representative of first feature horizontal height higher than second feature.Fisrt feature exists
Second feature " under ", " lower section " and " following " include fisrt feature right above second feature and oblique upper, or be merely representative of
First feature horizontal height is less than second feature.
Rotary compressor according to an embodiment of the present invention is described below with reference to Fig. 1-Fig. 3.Wherein, rotary compressor can
Think vertical compressor, or horizontal compressor.In the description below the application, using rotary compressor as vertical pressure
It is illustrated for contracting machine.
Rotary compressor according to an embodiment of the present invention, comprising: shell and compression mechanism 100.Compression mechanism 100 is located at
In shell, compression mechanism 100 includes cylinder assembly and crankshaft, and the axial ends of cylinder assembly is respectively equipped with base bearing 3 and countershaft
4 are held, cylinder assembly includes at least one cylinder 2, and cylinder 2 has cylinder chamber 21, is equipped with piston 22 in cylinder chamber 21, crankshaft runs through
Cylinder assembly, crankshaft include crankshaft body 11 and at least one eccentric part 12 for being located on crankshaft body 11, and piston 22 is set in
On eccentric part 12, cylinder 2 is equipped with sliding vane groove 23, and crankshaft body 11 is adjacent to main shaft along the direction contrary with crankshaft eccentric
Hold 3 and supplementary bearing 4 in one of them and when piston 22 is adjacent to eccentric part 12 along the direction contrary with crankshaft eccentric,
Radial clearance between the periphery wall of piston 22 and the internal perisporium of corresponding cylinder chamber 21 is δ, and eccentric part 12 is from sliding vane groove 23
Central axis along rotary compressor traffic direction rotate angle be θ when δ have minimum value δmin, θ satisfaction: 280 °≤θ≤
340°.Wherein, the angle θ is properly termed as aligning angle.
Specifically, for single cylinder rotary compressor, in assembling process, first base bearing 2 can be assembled in gas
Axial one end (for example, upper end in Fig. 1) of cylinder, then supplementary bearing 2 is assembled into the axial other end in cylinder (for example, in Fig. 1
Lower end), at this time by crankshaft body 11 along the direction contrary with crankshaft eccentric be adjacent to base bearing 3 and by piston 22 along with song
When the contrary direction of eccentric shaft is adjacent to eccentric part 12, between the periphery wall of piston 22 and the internal perisporium of corresponding cylinder chamber 21
Radial clearance be δ.Certainly, in assembling process, supplementary bearing 2 can also first be assembled to the above-mentioned other end (i.e. Fig. 1 in cylinder
In lower end), then by base bearing 3 assemble in above-mentioned one end (i.e. upper end in Fig. 1) of cylinder, at this time by crankshaft body 11 along with
The contrary direction of crankshaft eccentric is adjacent to supplementary bearing 4 and is adjacent to piston 22 partially along the direction contrary with crankshaft eccentric
When center portion 12, the radial clearance between the periphery wall of piston 22 and the internal perisporium of corresponding cylinder chamber 21 is δ.
Here, it should be noted that described " crankshaft eccentric direction " is referred to from crankshaft body 11 in the application
The heart is directed toward the direction at the center of eccentric part 12.
Rotary compressor according to an embodiment of the present invention, by setting central axis edge of the eccentric part 12 from sliding vane groove 23
When the angle, θ of the traffic direction rotation of rotary compressor is 280 °≤θ≤340 °, the periphery wall of piston 22 and corresponding cylinder
Radial clearance δ between the internal perisporium of chamber 21 has minimum value δmin, efficiently reduce rotary compressor in the process of running
Radial clearance fluctuation so that rotary compressor is in the process of running, when so that rotary compressor being run, piston 22 with
Radial clearance between cylinder 2 is in compared with the figure of merit always, and then can be by smallest radial gap deltaminWhat is be arranged is smaller, reduces
Friction loss simultaneously improves refrigerating capacity, greatly improves the Performance And Reliability of rotary compressor.
As shown in Figure 1, rotary compressor according to an embodiment of the present invention, comprising: shell (not shown go out) and compressor
Structure 100.
Wherein, shell may include the upper housing, main casing and lower case being sequentially connected from top to bottom, specifically, main
The top and bottom of shell are opened wide, and upper housing is connected to the top of main casing, and lower case is connected to the bottom of main casing, example
Such as, upper housing and lower case can be respectively welded to the top and bottom of main casing.Wherein, shell is preferably rotary structure.
Compression mechanism 100 is located in shell, and compression mechanism 100 includes cylinder assembly and crankshaft, and cylinder assembly includes at least
One cylinder 2, that is to say, that cylinder assembly may include one or more cylinders 2.When cylinder assembly includes a cylinder 2,
Rotary compressor can be single cylinder compressor, and when cylinder assembly includes multiple cylinders 2, rotary compressor can be multi-cylinder
Compressor can be equipped with middle partition between adjacent cylinder 2 for example, duplex cylinder compressor, three cylinder compressors etc..
Cylinder 2 has cylinder chamber 21, the piston 22 of eccentric rotary is equipped in cylinder chamber 21, crankshaft runs through cylinder assembly, bent
Axis includes crankshaft body 11 and at least one eccentric part 12 for being located on crankshaft body 11, and piston 22 is set on eccentric part 12.
Specifically, rotary compressor further includes motor (not shown go out), and motor is located in shell, motor include stator and
Rotor, stator is fixed on the inner wall of the housing, for example, stator can be fixed by modes such as interference fit, welding or rivetings
On shell.The axial ends of cylinder assembly is respectively equipped with base bearing 3 and supplementary bearing 4, for example, in the example of fig. 1, base bearing
3 are located at the upper end of cylinder assembly, and supplementary bearing 4 is located at the lower end of cylinder assembly.Specifically, base bearing 3 is located at the cylinder 2 of the top
Upper end, supplementary bearing 4 is located at the lower end of the cylinder 2 of bottom.One end (for example, lower end in Fig. 1) of crankshaft body 11 is run through
The other end (for example, upper end in Fig. 1) of base bearing 3, cylinder assembly and supplementary bearing 4, crankshaft body 11 is connected with rotor.
Referring to Fig. 2, cylinder 2 is equipped with sliding vane groove 23, the air entry 24 for sucking refrigerant and the row for refrigerant to be discharged
Port 25.The slide plate moved back and forth is equipped in sliding vane groove 23, the apex of slide plate is contacted with the periphery wall of corresponding piston 22.Specifically
Ground, the corresponding piston 22 of cylinder 2 cooperate with slide plate corresponding cylinder chamber 21 is separated into suction chamber and compression chamber.Rotary pressure
When contracting machine is run, rotor band dynamic crankshaft rotates, and the eccentric part 12 of crankshaft is rolled with piston 22, and slide plate is connected to 22 periphery of piston
On wall, moved back and forth in the sliding vane groove 23 of cylinder 2 under the promotion of piston 22.
Radial clearance between the periphery wall of piston 22 and the internal perisporium of corresponding cylinder chamber 21 is δ, and eccentric part 12 is from cunning
The central axis of film trap 23 along rotary compressor traffic direction rotate angle be θ when radial clearance δ have minimum value
δmin, θ satisfaction: 280 °≤θ≤340 °.That is, setting 280 °≤θ≤340 ° for aligning angle θ.Here, it needs to illustrate
It is that described " traffic direction of rotary compressor " refers in rotary compressor operational process in the application, crankshaft
The rotation direction of eccentric part 12.For example, in the figure 2 example, the traffic direction of rotary compressor refers to the inverse time in Fig. 2
Needle direction.
Thus, it is possible to reduce the fluctuation of the radial clearance of rotary compressor in the process of running, so that rotary compression
In the process of running, the radial clearance between piston 22 and cylinder 2 is in compared with the figure of merit machine always, so that the friction loss of compressor
It is in preferable equalization point with coolant leakage, and then can be by smallest radial gap deltaminWhat is be arranged is smaller, and efficiently avoiding can
The inordinate wear that can occur, it is stuck the problems such as, and reduce leakage of the refrigerant from radial clearance, greatly improve rotary
The Performance And Reliability of compressor.
Specifically, referring to Figures 1 and 2, the internal diameter of cylinder 2 is D, and the outer diameter of piston 22 is Dro, the internal diameter of piston 22 is
Dri, the eccentricity of crankshaft is e, one of them above-mentioned matching hole cooperated with crankshaft body 11 in base bearing 3 and supplementary bearing 4
Internal diameter is Db, the diameter of eccentric part 12 is Dse, crankshaft body 11 in base bearing 3 and supplementary bearing 4 it is above-mentioned one of them match
Diameter at conjunction is Dsb。
According to practical set technique, for single cylinder rotary compressor, base bearing 3 and cylinder 2 are assembled into the ban
Component, then when component and supplementary bearing 4 that base bearing 3 and cylinder 2 are assembled into assemble, base bearing 3 and crankshaft body 11 can be matched
The internal diameter of the matching hole of conjunction is set as Db, crankshaft body 11 is set as D with the diameter at 3 cooperation of base bearingsb.In the ban by countershaft
It holds 4 and is assembled into component with cylinder 2, then when the component and base bearing 3 that supplementary bearing 4 and cylinder 2 are assembled into assemble, it can be by supplementary bearing
The internal diameter of 4 matching holes cooperated with crankshaft body 11 is set as Db, crankshaft body 11 at 4 cooperation of supplementary bearing diameter be arranged
For Dsb。
For twin-tub rotation-type compressor, base bearing 3 and upper cylinder are first usually assembled into upper cylinder component, by countershaft
It holds 4 and is assembled into lower cylinder component with lower cylinder, finally fit together upper cylinder component and lower cylinder component, at this point, base bearing 3 and pair
Bearing 4 be it is completely equivalent, design scheme of the invention can be used simultaneously.That is, can be by base bearing 3 and crankshaft body
The internal diameter of the matching hole of 11 cooperations is set as Db, crankshaft body 11 is set as D with the diameter at 3 cooperation of base bearingsb, can also be with
D is set by the internal diameter for the matching hole that supplementary bearing 4 and crankshaft body 11 cooperateb, crankshaft body 11 at 3 cooperation of supplementary bearing
Diameter is set as Dsb.For convenience of description, in the description below the application, with base bearing 3 in single cylinder rotary compressor and song
The internal diameter for the matching hole that shaft body 11 cooperates is Db, crankshaft body 11 with the diameter at 3 cooperation of base bearing be DsbFor carry out
Explanation.
Specifically, in rotary compressor operational process, each friction of motion pair is provided with the gap for being used to form oil film,
Wherein, the gap between crankshaft body 11 and base bearing 3 is Cb:
Cb=Db-Dsb (1)
Gap between the eccentric part 12 and piston 22 of crankshaft is Ce:
Ce=Dri-Dse (2)
When the eccentric part 12 of crankshaft is coaxial with piston 22 and crankshaft body 11 and coaxial base bearing 3, cylinder 2, crankshaft exists
Radial clearance δ between the periphery wall of different rotational angle lower pistons 22 and the internal perisporium of cylinder chamber 210It is all the same:
δ0=(D-Dro-2e)/2 (3)
Due to the presence of foozle, rotary compressor is usually arranged base bearing 3 and cylinder 2 is not coaxial in assembly,
Guarantee that cylinder 2 is vented the radial clearance of side region with emphasis.It specifically, will be bent when assembling rotary compressor referring to Fig. 2
The side (for example, left side in Fig. 2) contrary with crankshaft eccentric of axis be adjacent in base bearing 3 and supplementary bearing 4 it is above-mentioned its
In one, and the side identical with crankshaft eccentric direction of piston 22 is adjacent to the eccentric part 12 of crankshaft, by the eccentric part of crankshaft
12 since the position of the central axis of sliding vane groove 23, along rotary compressor traffic direction (for example, the side counterclockwise in Fig. 2
To) rotation the angle θ when, set the radial clearance between the periphery wall of piston 22 and the internal perisporium of cylinder chamber 21 as minimum value.
Wherein, the offset of base bearing 3 is △:
△=δ0+(Cb+Ce)/2-δmin (4)
Inventor has found in the course of the research, when assembly, passes through offset base bearing 3, it is ensured that cylinder 2 is vented side region
Radial clearance, but simultaneously but also diameter of the eccentric part 12 of crankshaft at different rotational angle θ, between piston 22 and cylinder 2
Fluctuation is generated to gap delta, as shown in the static clearance curve in Fig. 3 and Fig. 5.On the other hand, rotary compressor is in practical fortune
Oil film thickness, piston 22 and crankshaft when turning, due to the effect of the load such as gas load, between base bearing 3 and crankshaft body 11
Eccentric part 12 between oil film thickness will change, to be had an impact to the radial clearance between piston 22 and cylinder 2,
It influences size as shown in the dynamic clearance curve in Fig. 3 and Fig. 5.Rotary compressor in the process of running, piston 22 and gas
Practical radial clearance between cylinder 2 is the comprehensive function of above-mentioned static clearance and dynamic clearance, such as the total backlash in Fig. 3 and Fig. 5
Shown in curve.
In the related technology, usually by eccentric part 12 from the central axis of sliding vane groove 23 along the traffic direction of rotary compressor
The angle (i.e. aligning angle) of rotation meets: corresponding radial clearance is set as most when 240 °≤θ≤270 ° (such as θ=255 ° etc.)
Small value, as shown in Figure 4.From figure 5 it can be seen that the practical radial clearance between piston 22 and cylinder 2 in the related technology exists
It is fluctuated under the different rotational angles of the eccentric part 12 of crankshaft very greatly, so that rotary compressor in the related technology is in eccentric part 12
Practical radial clearance in most of rotational angle range is not the setting model for the minimum value that radial clearance is limited compared with advantage
It encloses, reduces the performance of rotary compressor.
Inventor has found that rotary compressor is in actual motion in the course of the research, under the effect of the loads such as gas force,
Crankshaft and piston 22 will be mobile approximately along resultant direction, eccentric part 12 of the dynamic clearance between piston 22 and cylinder 2 in crankshaft
Rotational angle be 280 °~340 ° between form maximum, by aligning angle θ be arranged between above-mentioned rotational angle range when,
That is the static clearance between piston 22 and cylinder 2 can be made to adjust when so that aligning angle θ meeting 280 °≤θ≤340 °
The corresponding angle in core angle forms minimum in the corresponding approximate angle in aligning angle, so as to so that rotary compressor in reality
Practical radial clearance fluctuation when operation between piston 22 and cylinder 2 greatly reduces, so that practical when rotary compressor is run
Radial clearance is in compared with the figure of merit always, and then can be by smallest radial gap deltaminWhat is be arranged is smaller, reduces friction loss and mentions
Refrigerating capacity has been risen, the Performance And Reliability of rotary compressor is greatly improved.
Wherein, it is influenced by each mechanical dimension of rotary compressor, the dynamic of the rotary compressor of different mechanical dimensions
When gap forms maximum, 12 rotational angle of eccentric part of crankshaft changes within the scope of 280 °~340 °.Due to crankshaft body 11
It rubs the presence of secondary oil film with rub secondary oil film, the eccentric part 12 of crankshaft and the piston 22 of base bearing 3, smallest radial gap deltaminInstitute
When approximate angle of the angle, θ when dynamic clearance forms maximum changes, gas when rotary compressor can't be caused to run
The acute variation of practical radial clearance between cylinder 2 and piston 22.As a result, by eccentric part 12 from the central axis edge of sliding vane groove 23
Corresponding radial clearance is set as minimum value when the angle, θ of the traffic direction rotation of rotary compressor is 280 °≤θ≤340 °,
The influence that can reduce manufacture fluctuation is conducive to the consistency for improving manufacture, improves the production efficiency of rotary compressor, drops
Low production cost.
It is understood that the specific value of aligning angle θ can run according to the rotary compressor of different model
Cheng Zhong, the dynamic clearance between piston 22 and cylinder 2 forms corresponding angle adjusted design when maximum, for example, working as piston 22
It, can be by eccentric part 12 from slide plate when dynamic clearance between cylinder 2 forms maximum when crank rotation angle is 310 °
The central axis of slot 23 rotates 310 °, 305 °, 315 ° along the angle (i.e. aligning angle) that the traffic direction of rotary compressor rotates
Corresponding radial clearance is set as minimum value whens equal.Wherein, preferably eccentric part 12 is rotated from the central axis edge of sliding vane groove 23
Corresponding radial clearance is set as minimum value whens 310 ° of angle (i.e. aligning angle) rotation of traffic direction rotation of formula compressor etc..
According to some embodiments of the present invention, the minimum value δ of radial clearanceminMeet: 10 μm≤δmin≤20μm.It is specific
Numerical value can be according to the concrete specification model adjusted design of rotary compressor.For example, the minimum value δ of radial clearanceminIt can be into
One step meets: δmin=10 μm, δmin=15 μm, δmin=20 μm etc..Thus, it is possible to which rotary compressor is avoided abnormal mill occur
Phenomena such as damaging, is stuck, reduces the friction loss of rotary compressor, improves the reliability of rotary compressor.And it can be with
The leakage for effectively reducing refrigerant, improves the refrigerating capacity of rotary compressor, to effectively improve rotary compressor
Performance.
According to some embodiments of the present invention, the outer diameter D of the internal diameter D of cylinder 2, piston 22ro, piston 22 internal diameter Dri, it is bent
The internal diameter D for the matching hole that eccentric amount e, base bearing 3 and the crankshaft body 11 of axis cooperateb, eccentric part 12 diameter Dse, crankshaft body
11 with the diameter D at 3 supplementary bearing of base bearing, 4 cooperationsbMeet: | D-Dro-2e-2δmin+0.625(Dri+Db-Dse-Dsb)|≤10
μm。
Wherein, in the process of running, the fluctuating range of the static clearance between piston 22 and cylinder 2 is rotary compressor
Ws, the fluctuating range of the dynamic clearance between piston 22 and cylinder 2 is Wd.Studies have shown that the fluctuation width of static clearance meets:
Ws=2 △ (6)
The fluctuating range W of dynamic clearancedIt is related to the factors such as the operating condition of rotary compressor, discharge capacity, dynamic clearance
Fluctuating range Wd approximation meet: Wd=0.375 (Cb+Ce) (7)
D、Dro、Dri、e、Db、Dse、Dsb, δ min meet: | D-Dro-2e-2δmin+0.625(Dri+Db-Dse-Dsb)|≤10μm
When, it may make that the fluctuating range of static clearance is WsWith the fluctuating range W of dynamic clearancedIt is approximately equal, so as to further
Reduce the fluctuation of practical radial clearance in rotary compressor operational process, and then further increases rotary compressor
Performance.
Optionally, D, Dro、Dri、e、Db、Dse、Dsb, δ min further satisfaction: D-Dro-2e-2δmin+0.625(Dri+Db-
Dse-Dsb)=0.W at this times=Wd.The performance of rotary compressor is further improved as a result,.
According to some embodiments of the present invention, rotary compressor is constant speed compressor, or frequency-changeable compressor.
Rotary compressor according to an embodiment of the present invention greatly improves the reliability and property of rotary compressor
Energy.
In the description of this specification, reference term " one embodiment ", " some embodiments ", " illustrative examples ",
The description of " example ", " specific example " or " some examples " etc. means specific features described in conjunction with this embodiment or example, knot
Structure, material or feature are included at least one embodiment or example of the invention.In the present specification, to above-mentioned term
Schematic representation may not refer to the same embodiment or example.Moreover, specific features, structure, material or the spy of description
Point can be combined in any suitable manner in any one or more of the embodiments or examples.
Although an embodiment of the present invention has been shown and described, it will be understood by those skilled in the art that: not
A variety of change, modification, replacement and modification can be carried out to these embodiments in the case where being detached from the principle of the present invention and objective, this
The range of invention is defined by the claims and their equivalents.
Claims (8)
1. a kind of rotary compressor characterized by comprising
Shell；
Compression mechanism, the compression mechanism are located in the shell, and the compression mechanism includes cylinder assembly and crankshaft, the gas
The axial ends of cylinder component is respectively equipped with base bearing and supplementary bearing, and the cylinder assembly includes at least one cylinder, the cylinder
With cylinder chamber, piston is equipped in the cylinder chamber, the crankshaft runs through the cylinder assembly, and the crankshaft includes crankshaft body
With at least one eccentric part being located on the crankshaft body, the piston is set on the eccentric part, is set on the cylinder
There is sliding vane groove,
The crankshaft body is adjacent in the base bearing and the supplementary bearing along the direction contrary with the crankshaft eccentric
One of them and when the piston is adjacent to the eccentric part along the direction contrary with the crankshaft eccentric, the work
Radial clearance between the periphery wall of plug and the internal perisporium of the corresponding cylinder chamber is δ, and the eccentric part is from the sliding vane groove
Central axis along the angle that the traffic direction of the rotary compressor rotates be θ when the δ there is minimum value δmin, the θ
Meet:
280°≤θ≤340°；
The internal diameter of the cylinder is D, and the outer diameter of the piston is Dro, the internal diameter of the piston is Dri, the eccentricity of the crankshaft
For e, the internal diameter of one of them matching hole cooperated with the crankshaft body in the base bearing and the supplementary bearing is
Db, the diameter of the eccentric part is Dse, the crankshaft body in the base bearing and the supplementary bearing described in wherein one
Diameter at a cooperation is Dsb, described D, Dro、Dri、e、Db、Dse、Dsb、δminMeet:
|D-Dro-2e-2δmin+0.625(Dri+Db-Dse-Dsb)|≤10μm。
2. rotary compressor according to claim 1, which is characterized in that the θ further satisfaction: θ=310 °.
3. rotary compressor according to claim 1, which is characterized in that the minimum value δ of the radial clearanceminMeet:
10μm≤δmin≤20μm。
4. rotary compressor according to claim 1, which is characterized in that described D, Dro、Dri、e、Db、Dse、Dsb、δmin
Further satisfaction:
D-Dro-2e-2δmin+0.625(Dri+Db-Dse-Dsb)=0.
5. rotary compressor according to claim 1, which is characterized in that the rotary compressor is single cylinder compression
Machine.
6. rotary compressor according to claim 1, which is characterized in that the rotary compressor is twin-tub compression
Machine.
7. rotary compressor according to claim 1, which is characterized in that the rotary compressor is constant speed compression
Machine.
8. rotary compressor according to claim 1, which is characterized in that the rotary compressor is frequency conversion compression
Machine.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201611095257.5A CN107061273B (en) | 2016-12-01 | 2016-12-01 | Rotary compressor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611095257.5A CN107061273B (en) | 2016-12-01 | 2016-12-01 | Rotary compressor |
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| CN107061273B true CN107061273B (en) | 2019-09-06 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109026698B (en) * | 2018-08-08 | 2019-09-03 | 珠海凌达压缩机有限公司 | A kind of compressor |
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| JP2000213484A (en) * | 1999-01-21 | 2000-08-02 | Daikin Ind Ltd | Rotary compressor |
| CN102094823A (en) * | 2009-12-10 | 2011-06-15 | 广东美芝制冷设备有限公司 | Cylinder assembly and core-adjusting method for cylinder of double-cylinder rotary compressor |
| CN202117928U (en) * | 2011-06-14 | 2012-01-18 | 广东美芝制冷设备有限公司 | Capacitance variable type rotary compressor |
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| CN102444582A (en) * | 2010-09-30 | 2012-05-09 | 广东美芝制冷设备有限公司 | Rotary type compressor |
| CN103782037A (en) * | 2012-06-01 | 2014-05-07 | 松下电器产业株式会社 | Rotary compressor |
| CN206246363U (en) * | 2016-12-01 | 2017-06-13 | 广东美芝制冷设备有限公司 | Rotary compressor |
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2016
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| JP2000213484A (en) * | 1999-01-21 | 2000-08-02 | Daikin Ind Ltd | Rotary compressor |
| CN102094823A (en) * | 2009-12-10 | 2011-06-15 | 广东美芝制冷设备有限公司 | Cylinder assembly and core-adjusting method for cylinder of double-cylinder rotary compressor |
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