CN107061273A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- CN107061273A CN107061273A CN201611095257.5A CN201611095257A CN107061273A CN 107061273 A CN107061273 A CN 107061273A CN 201611095257 A CN201611095257 A CN 201611095257A CN 107061273 A CN107061273 A CN 107061273A
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- Prior art keywords
- rotary compressor
- cylinder
- piston
- eccentric part
- bent axle
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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
- F04C18/356—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 compressor, including：Housing and compression mechanism, compression mechanism is located in housing, compression mechanism includes cylinder assembly and bent axle, cylinder assembly includes at least one cylinder, cylinder has cylinder chamber, piston is provided with cylinder chamber, bent axle runs through cylinder assembly, bent axle includes crankshaft body and at least one eccentric part being located on crankshaft body, piston is set on eccentric part, cylinder is provided with vane slot, radial clearance between the periphery wall of piston and the internal perisporium of corresponding cylinder chamber is δ, δ has minimum value δ when the angle that traffic direction of the eccentric part from the central axis of vane slot along rotary compressor is rotated is θmin, θ satisfactions：280°≤θ≤340°., can be by smallest radial gap delta according to the rotary compressor of the present inventionminWhat is set is smaller, reduces friction loss and improves refrigerating capacity, drastically increases the Performance And Reliability of rotary compressor.
Description
Technical field
The present invention relates to Compressor Technology field, more particularly, to a kind of rotary compressor.
Background technology
In correlation technique, compressor such as rotary compressor as a kind of high-precision engineering goods, its piston it is outer
Radial clearance between perisporium and the internal perisporium of cylinder chamber is most important for compressor performance and reliability.If gap is set
It is too small, due to the effect of the factors such as foozle, operating load, stuck compressor, inordinate wear or friction loss may be caused
It is excessive；If gap sets excessive, it will be increased dramatically by the refrigerant of the leakage of radial clearance, and cause compressor performance to decline.
In addition, radial clearance sets unreasonable, rotary compressor friction loss and coolant leakage can not be in a better balance point,
It is unfavorable for the lifting of compressor performance.
The content of the invention
It is contemplated that at least solving one of technical problem present in prior art.Therefore, one object of the present invention
It is to propose a kind of rotary compressor, the reliability of the rotary compressor is high and performance is high.
According to the rotary compressor of the present invention, including：Housing；Compression mechanism, the compression mechanism is located at the housing
Interior, the compression mechanism includes cylinder assembly and bent axle, and the axial two ends of the cylinder assembly are respectively equipped with base bearing and countershaft
Hold, the cylinder assembly includes at least one cylinder, the cylinder, which has, is provided with piston in cylinder chamber, the cylinder chamber, described
Bent axle runs through the cylinder assembly, at least one bias that the bent axle includes crankshaft body and is located on the crankshaft body
Portion, the piston is set on the eccentric part, and the cylinder is provided with vane slot, by crankshaft body edge and the bent axle
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 crankshaft eccentric direction in opposite direction is adjacent to the eccentric part, the periphery wall of the piston is interior with the corresponding cylinder chamber
Radial clearance between perisporium is δ, fortune of the eccentric part from the central axis of the vane slot along the rotary compressor
The δ has minimum value δ when the angle that line direction is rotated is θmin, the θ satisfactions：280°≤θ≤340°.
According to the rotary compressor of the present invention, by setting eccentric part from the central axis of vane slot along rotary compression
When the angle, θ that the traffic direction of machine is rotated is 280 °≤θ≤340 °, the internal perisporium of the periphery wall of piston and corresponding cylinder chamber it
Between radial clearance δ there is minimum value δmin, efficiently reduce the ripple 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 so that when rotary compressor is run, between the radial direction between piston and cylinder
Gap is in compared with the figure of merit all the time, and then can be by smallest radial gap deltaminWhat is set is smaller, reduces friction loss and improves system
Cold, drastically increases the Performance And Reliability of rotary compressor.
In addition, can also have technical characteristic additional as follows according to the rotary compressor of the present invention：
According to some embodiments of the present invention, the θ is further met：θ=310 °.
Specifically, the minimum value δ of the radial clearanceminMeet：10μm≤δmin≤20μm。
According to some embodiments of the present invention, the internal diameter of the cylinder is D, and the external diameter of the piston is Dro, the piston
Internal diameter be Dri, the offset of the bent axle be in e, the base bearing and the supplementary bearing it is described one of them with the song
The internal diameter for the mating holes that shaft body coordinates is Db, a diameter of D of the eccentric partse, the crankshaft body with the base bearing
With a diameter of D 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。
Alternatively, described D, Dro、Dri、e、Db、Dse、Dsb, δ min further meet：
D-Dro-2e-2δmin+0.625(Dri+Db-Dse-Dsb)=0.
Alternatively, the rotary compressor is single cylinder compressor.
Alternatively, the rotary compressor is duplex cylinder compressor.
Alternatively, the rotary compressor is constant speed compressor.
Alternatively, the rotary compressor is frequency-changeable compressor.
The additional aspect and advantage of the present invention will be set forth in part in the description, and will partly become from the following description
Obtain substantially, or recognized by the practice of the present invention.
Brief description of the drawings
The above-mentioned and/or additional aspect and advantage of the present invention will become from description of the accompanying drawings below to embodiment is combined
Substantially and be readily appreciated that, wherein：
Fig. 1 is the cut-away view of the compression mechanism of rotary compressor according to embodiments of the present invention；
Fig. 2 is the schematic diagram of the radial clearance setting of rotary compressor according to embodiments of the present invention；
Fig. 3 is the change of rotary compressor according to embodiments of the present invention dynamic clearance and static clearance in the process of running
Change curve map；
Fig. 4 is the schematic diagram that sets of radial clearance of the rotary compressor in correlation technique；
Fig. 5 is rotary compressor in correlation technique dynamic clearance and the change curve of static clearance in the process of running
Figure.
Reference：
Compression mechanism 100,
Crankshaft body 11, eccentric part 12,
Cylinder 2, cylinder chamber 21, piston 22, vane slot 23, air entry 24, exhaust outlet 25,
Base bearing 3, supplementary bearing 4.
Embodiment
Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein from beginning to end
Same or similar label represents same or similar element or the element with same or like function.Below with reference to attached
The embodiment of figure description is exemplary, is only used for explaining the present invention, and is not considered as limiting the invention.
In the description of the invention, it is to be understood that term " " center ", " on ", " under ", "front", "rear", " left side ",
" right side ", " vertical ", " level ", " top ", " bottom ", " interior ", " outer ", " clockwise ", " counterclockwise ", " axial direction ", " radial direction ", " circumference "
Deng instruction orientation or position relationship be based on orientation shown in the drawings or position relationship, be for only for ease of description the present invention and
Simplify description, rather than indicate or imply that the device or element of meaning there must be specific orientation, with specific azimuth configuration
And operation, therefore be not considered as limiting the invention.In addition, term " first ", " second " are only used for describing purpose, without
It is understood that to indicate or imply relative importance or the implicit quantity for indicating indicated technical characteristic.Thus, define " the
One ", one or more this feature can be expressed or be implicitly included to the feature of " second ".In the description of the invention,
Unless otherwise indicated, " multiple " are meant that two or more.
In the description of the invention, it is necessary to illustrate, unless otherwise clearly defined and limited, term " installation ", " phase
Even ", " connection " should be interpreted broadly, for example, it may be being fixedly connected or being detachably connected, or be integrally connected；Can
To be mechanical connection or electrical connection；Can be joined directly together, can also be indirectly connected to by intermediary, Ke Yishi
The connection of two element internals.For the ordinary skill in the art, with concrete condition above-mentioned term can be understood at this
Concrete meaning in invention.
In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature it " on " or it " under "
Can directly it be contacted including the first and second features, it is not direct contact but by it that can also include the first and second features
Between other characterisation contact.Moreover, fisrt feature second feature " on ", " top " and " above " to include first special
Levy directly over second feature and oblique upper, or be merely representative of fisrt feature level height higher than second feature.Fisrt feature exists
Second feature " under ", " lower section " and " following " fisrt feature that includes are directly over second feature and oblique upper, or be merely representative of
Fisrt feature level height is less than second feature.
Rotary compressor according to embodiments 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
Illustrated exemplified by contracting machine.
Rotary compressor according to embodiments of the present invention, including：Housing and compression mechanism 100.Compression mechanism 100 is located at
In housing, compression mechanism 100 includes cylinder assembly and bent axle, and the axial two ends of cylinder assembly are respectively equipped with base bearing 3 and countershaft
4 are held, cylinder assembly includes at least one cylinder 2, cylinder 2, which has, is provided with piston 22 in cylinder chamber 21, cylinder chamber 21, bent axle runs through
Cylinder assembly, bent axle includes crankshaft body 11 and at least one eccentric part 12 being located on crankshaft body 11, and piston 22 is set in
On eccentric part 12, cylinder 2 is provided with vane slot 23, and crankshaft body 11 is adjacent into main shaft along the direction in opposite direction with crankshaft eccentric
Hold 3 and supplementary bearing 4 in one of them and by piston 22 along the direction in opposite direction with crankshaft eccentric be adjacent to eccentric part 12 when,
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 vane slot 23
δ has minimum value δ when the angle that traffic direction of the central axis along rotary compressor is rotated is θmin, θ satisfactions：280°≤θ≤
340°.Wherein, θ angles are 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), now by crankshaft body 11 along the direction in opposite direction with crankshaft eccentric be adjacent to base bearing 3 and by piston 22 along with song
When eccentric shaft direction in opposite direction 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 first can also be assembled into the above-mentioned other end (i.e. Fig. 1 in cylinder
In lower end), then base bearing 3 is assembled in above-mentioned one end (i.e. upper end in Fig. 1) of cylinder, now by crankshaft body 11 along with
Crankshaft eccentric direction in opposite direction is adjacent to supplementary bearing 4 and is adjacent to piston 22 partially along the direction in opposite direction with crankshaft eccentric
During 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 is necessary to which " crankshaft eccentric direction " described in explanation, the application is referred to from crankshaft body 11
The heart points to the direction at the center of eccentric part 12.
Rotary compressor according to embodiments of the present invention, by setting central axis edge of the eccentric part 12 from vane slot 23
When the angle, θ that the traffic direction of rotary compressor is rotated 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 so that rotary compressor run when, piston 22 with
Radial clearance between cylinder 2 is in compared with the figure of merit all the time, and then can be by smallest radial gap deltaminWhat is set is smaller, reduces
Friction loss simultaneously improves refrigerating capacity, drastically increases the Performance And Reliability of rotary compressor.
As shown in figure 1, rotary compressor according to embodiments of the present invention, including：Housing (not shown) and compressor
Structure 100.
Wherein, housing can include upper shell, main casing and the lower house being sequentially connected from top to bottom, specifically, main
The top and bottom of housing are opened wide, and upper shell is connected to the top of main casing, and lower house is connected to the bottom of main casing, example
Such as, upper shell and lower house can be respectively welded to the top and bottom of main casing.Wherein, housing is preferably rotary structure.
Compression mechanism 100 is located in housing, and compression mechanism 100 includes cylinder assembly and bent axle, and cylinder assembly is included at least
One cylinder 2, that is to say, that cylinder assembly can 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, for example, median septum can be provided between duplex cylinder compressor, three cylinder compressors etc., adjacent cylinder 2.
Cylinder 2 has the piston 22 that eccentric rotary is provided with cylinder chamber 21, cylinder chamber 21, and bent axle runs through cylinder assembly, bent
Axle includes crankshaft body 11 and at least one eccentric part 12 being located on crankshaft body 11, and piston 22 is set on eccentric part 12.
Specifically, rotary compressor also include motor (not shown), motor is located in housing, motor include stator and
Rotor, stator is fixed on the inwall of housing, for example, stator can be fixed by modes such as interference fit, welding or rivetings
On housing.The axial two ends of cylinder assembly are 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 be located at bottom cylinder 2 lower end.One end (for example, lower end in Fig. 1) of crankshaft body 11 is run through
Base bearing 3, cylinder assembly and supplementary bearing 4, the other end (for example, upper end in Fig. 1) of crankshaft body 11 are connected with rotor.
Reference picture 2, cylinder 2 is provided with vane slot 23, the air entry 24 for sucking refrigerant and the row for discharging refrigerant
Gas port 25.Reciprocating slide plate is provided with vane slot 23, the tip of slide plate is contacted with the periphery wall of corresponding piston 22.Specifically
Ground, the corresponding piston 22 of cylinder 2 coordinates corresponding cylinder chamber 21 being separated into suction muffler and compression chamber with slide plate.Rotary pressure
When contracting machine is run, rotor banding dynamic crankshaft rotation, the eccentric part 12 of bent axle is rolled with piston 22, and slide plate is connected to the periphery of piston 22
On wall, moved back and forth under the promotion of piston 22 in the vane slot 23 of cylinder 2.
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
Radial clearance δ has minimum value when the angle that traffic direction of the central axis of film trap 23 along rotary compressor is rotated is θ
δmin, θ satisfactions：280°≤θ≤340°.That is, aligning angle θ is set into 280 °≤θ≤340 °.Here, it is necessary to explanation
It is that described " traffic direction of rotary compressor " is referred in rotary compressor running in the application, bent axle
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
Pin 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 all the time so that the friction loss of compressor
Preferably equalization point, and then can be by smallest radial gap delta is in coolant leakageminWhat is set is smaller, and efficiently avoid can
The inordinate wear that can occur, it is stuck the problems such as, and reduce refrigerant from the leakage at radial clearance, drastically increase rotary
The Performance And Reliability of compressor.
Specifically, referring to Figures 1 and 2, the internal diameter of cylinder 2 is D, and the external diameter of piston 22 is Dro, the internal diameter of piston 22 is
Dri, the offset of bent axle is one of them above-mentioned mating holes coordinated with crankshaft body 11 in e, base bearing 3 and supplementary bearing 4
Internal diameter is Db, a diameter of D of eccentric part 12se, crankshaft body 11 with base bearing 3 and supplementary bearing 4 it is above-mentioned one of them match somebody with somebody
A diameter of D at conjunctionsb。
According to practical set technique, for single cylinder rotary compressor, base bearing 3 is assembled into cylinder 2 in the ban
Component, then the component that base bearing 3 and cylinder 2 are assembled into supplementary bearing 4 when assembling, and can match somebody with somebody base bearing 3 with crankshaft body 11
The internal diameter of the mating holes of conjunction is set to Db, crankshaft body 11 with the diameter at the cooperation of base bearing 3 is set to Dsb.In the ban by countershaft
Hold 4 and be assembled into component with cylinder 2, then the component that supplementary bearing 4 and cylinder 2 are assembled into base bearing 3 when assembling, can be by supplementary bearing
The internal diameter of 4 mating holes coordinated with crankshaft body 11 is set to Db, crankshaft body 11 with the cooperation of supplementary bearing 4 diameter set
For Dsb。
For twin-tub rotation-type compressor, base bearing 3 and upper cylinder are first generally assembled into upper cylinder component, by countershaft
Lower cylinder component is assembled into hold 4 with lower cylinder, finally fit together upper cylinder component and lower cylinder component, now, base bearing 3 and pair
Bearing 4 is completely equivalent, and the design of the present invention can be used simultaneously.That is, can be by base bearing 3 and crankshaft body
The internal diameter of 11 mating holes coordinated is set to Db, crankshaft body 11 with the diameter at the cooperation of base bearing 3 is set to Dsb, can also
The internal diameter for the mating holes that supplementary bearing 4 and crankshaft body 11 are coordinated is set to Db, crankshaft body 11 with the cooperation of supplementary bearing 3
Diameter is set to Dsb.For convenience of describing, in the description below the application, with base bearing 3 in single cylinder rotary compressor and song
The internal diameter for the mating holes that shaft body 11 coordinates is Db, crankshaft body 11 with a diameter of D at the cooperation of base bearing 3sbExemplified by carry out
Explanation.
Specifically, in rotary compressor running, each friction of motion pair is provided with the gap for forming 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 bent axle is Ce：
Ce=Dri-Dse (2)
The eccentric part 12 of bent axle and piston 22 be coaxial and when crankshaft body 11 and coaxial base bearing 3, cylinder 2, bent axle exists
Radial clearance δ between the periphery wall of different rotational angle lower pistons 22 and the internal perisporium of cylinder chamber 210All same：
δ0=(D-Dro-2e)/2 (3)
Due to the presence of foozle, rotary compressor generally sets base bearing 3 and cylinder 2 not coaxial in assembling,
Ensure that cylinder 2 is vented the radial clearance of side region with emphasis.Specifically, reference picture 2, when assembling rotary compressor, by song
The side (for example, left side in Fig. 2) in opposite direction with crankshaft eccentric of axle be adjacent in base bearing 3 and supplementary bearing 4 it is above-mentioned its
In one, and by the eccentric part 12 that bent axle is adjacent to crankshaft eccentric direction identical side of piston 22, by the eccentric part of bent axle
12 since the position of the central axis of vane slot 23, along rotary compressor traffic direction (for example, the side counterclockwise in Fig. 2
To) rotate θ angles 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 research process, during assembling, by offseting base bearing 3, it is ensured that cylinder 2 is vented side region
Radial clearance, but simultaneously also cause bent axle eccentric part 12 under different rotational angle θ, the footpath between piston 22 and cylinder 2
Fluctuation is produced to gap delta, as shown in the static clearance curve in Fig. 3 and Fig. 5.On the other hand, rotary compressor is in actual fortune
When turning, due to the effect of the load such as gas load, oil film thickness, piston 22 and bent axle between base bearing 3 and crankshaft body 11
Eccentric part 12 between oil film thickness will change so that between piston 22 and cylinder 2 radial clearance produce influence,
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
Actual radial clearance between cylinder 2 is the total backlash in the comprehensive function of above-mentioned static clearance and dynamic clearance, such as Fig. 3 and Fig. 5
Shown in curve.
In correlation technique, the traffic direction generally by eccentric part 12 from the central axis of vane slot 23 along rotary compressor
The angle (i.e. aligning angle) of rotation is met:Corresponding radial clearance is set to most when 240 °≤θ≤270 ° (such as θ=255 °)
Small value, as shown in Figure 4.From figure 5 it can be seen that the actual radial clearance between piston 22 and cylinder 2 in correlation technique exists
Fluctuated under the different rotational angles of the eccentric part 12 of bent axle very big so that the rotary compressor in correlation technique is in eccentric part 12
Actual 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
Enclose, reduce the performance of rotary compressor.
Inventor has found that rotary compressor is in actual motion, under the effect of the loads such as gas force in research process,
Crankshaft and piston 22 will be moved approximately along resultant direction, eccentric part 12 of the dynamic clearance between piston 22 and cylinder 2 in bent axle
Rotational angle be to form maximum between 280 °~340 °, when aligning angle θ is arranged between above-mentioned rotational angle range,
That is so that when aligning angle θ meets 280 °≤θ≤340 °, the static clearance between piston 22 and cylinder 2 can be caused to adjust
The corresponding angle in core angle forms minimum in the corresponding approximate angle in aligning angle, so as to so that rotary compressor is in reality
Actual radial clearance fluctuation during operation between piston 22 and cylinder 2 is greatly reduced so that actual when rotary compressor is run
Radial clearance is in compared with the figure of merit all the time, and then can be by smallest radial gap deltaminWhat is set is smaller, reduces friction loss and carries
Refrigerating capacity has been risen, the Performance And Reliability of rotary compressor is drastically increased.
Wherein, influenceed by each mechanical dimension of rotary compressor, the dynamic of the rotary compressor of different mechanical dimensions
When gap forms maximum, the rotational angle of eccentric part 12 of bent axle changes in the range of 280 °~340 °.Due to crankshaft body 11
With the presence of the friction pair oil film of base bearing 3, the eccentric part 12 of bent axle and the friction pair oil film of piston 22, smallest radial gap deltaminInstitute
During approximate angle change when angle, θ is in dynamic clearance formation maximum, gas when can't cause the rotary compressor to run
The acute variation of actual radial clearance between cylinder 2 and piston 22.Thus, by eccentric part 12 from the central axis edge of vane slot 23
Corresponding radial clearance is set to minimum value when the angle, θ that the traffic direction of rotary compressor is rotated is 280 °≤θ≤340 °,
The influence of manufacture fluctuation can be reduced, be conducive to improving the uniformity manufactured, improve the production efficiency of rotary compressor, drop
Low production cost.
It is understood that aligning angle θ concrete numerical value can run according to the rotary compressor of different model
Cheng Zhong, the dynamic clearance between piston 22 and cylinder 2 forms corresponding angle adjustment design during maximum, for example, when piston 22
, can be by eccentric part 12 from slide plate when dynamic clearance between cylinder 2 forms maximum when crank rotation angle is 310 °
The angle (i.e. aligning angle) that traffic direction of the central axis of groove 23 along rotary compressor is rotated rotates 310 °, 305 °, 315 °
Deng when corresponding radial clearance be set to minimum value.Wherein, preferably eccentric part 12 is rotated from the central axis edge of vane slot 23
Corresponding radial clearance is set to minimum value when the angle (i.e. aligning angle) that the traffic direction of formula compressor is rotated rotates 310 ° etc..
According to some embodiments of the present invention, the minimum value δ of radial clearanceminMeet：10μm≤δmin≤20μm.Its is specific
Numerical value can be according to the The concrete specification model adjusted design of rotary compressor.For example, the minimum value δ of radial clearanceminIt can enter
One step is met：δmin=10 μm, δmin=15 μm, δmin=20 μm etc..Thus, it is possible to avoid rotary compressor from abnormal mill occur
The phenomenon such as damage, stuck, reduces the friction loss of rotary compressor, improves the reliability of rotary compressor.And can be with
Effectively reduce the leakage of refrigerant, the refrigerating capacity of rotary compressor is improved, so as to be effectively improved rotary compressor
Performance.
According to some embodiments of the present invention, the internal diameter D of cylinder 2, the outer diameter D of piston 22ro, piston 22 internal diameter Dri, it is bent
The internal diameter D for the mating holes that eccentric amount e, the base bearing 3 of axle coordinate with crankshaft body 11b, eccentric part 12 diameter Dse, crankshaft body
11 with the diameter D at the cooperation of 3 supplementary bearing of base bearing 4sbMeet：|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.Research shows that the fluctuation width of static clearance is met：
Ws=2 △ (6)
The fluctuating range W of dynamic clearancedThe factors such as operating condition, discharge capacity to rotary compressor are related, dynamic clearance
Fluctuating range Wd approximately 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, the fluctuating range that may be such that static clearance is WsWith the fluctuating range W of dynamic clearancedApproximately equal, so as to further
Reduce the fluctuation of actual radial clearance in rotary compressor running, and then further increasing rotary compressor
Performance.
Alternatively, D, Dro、Dri、e、Db、Dse、Dsb, δ min further meet：D-Dro-2e-2δmin+0.625(Dri+Db-
Dse-Dsb)=0.Now Ws=Wd.Thus, the performance of rotary compressor is further improved.
According to some embodiments of the present invention, rotary compressor is constant speed compressor, or frequency-changeable compressor.
Rotary compressor according to embodiments of the present invention, drastically increases 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 to combine specific features, the knot that the embodiment or example are described
Structure, material or feature are contained at least one embodiment of the present invention or example.In this manual, to above-mentioned term
Schematic representation is not necessarily referring to identical embodiment or example.Moreover, specific features, structure, material or the spy of description
Point can in an appropriate manner be combined in any one or more embodiments or example.
Although an embodiment of the present invention has been shown and described, it will be understood by those skilled in the art that：Not
In the case of departing from the principle and objective of the present invention a variety of change, modification, replacement and modification can be carried out to these embodiments, this
The scope of invention is limited by claim and its equivalent.
Claims (9)
1. a kind of rotary compressor, it is characterised in that including：
Housing；
Compression mechanism, the compression mechanism is located in the housing, and the compression mechanism includes cylinder assembly and bent axle, the gas
The axial two ends of cylinder component are respectively equipped with base bearing and supplementary bearing, and the cylinder assembly includes at least one cylinder, the cylinder
With cylinder chamber, piston is provided with the cylinder chamber, the bent axle runs through the cylinder assembly, and the bent axle 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 vane slot,
The crankshaft body is adjacent in the base bearing and the supplementary bearing along the direction in opposite direction with the crankshaft eccentric
One of them and by the piston along the direction in opposite direction with the crankshaft eccentric be adjacent to the eccentric part when, 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 vane slot
The angle that rotates of traffic direction of the central axis along the rotary compressor when being θ the δ there is minimum value δmin, the θ
Meet：
280°≤θ≤340°。
2. rotary compressor according to claim 1, it is characterised in that the θ is further met：θ=310 °.
3. rotary compressor according to claim 1, it is characterised in that the minimum value δ of the radial clearanceminMeet：
10μm≤δmin≤20μm。
4. the rotary compressor according to any one of claim 1-3, it is characterised in that the internal diameter of the cylinder is D,
The external diameter of the piston is Dro, the internal diameter of the piston is Dri, the offset of the bent axle is e, the base bearing and the pair
The internal diameter of one of them mating holes coordinated with the crankshaft body in bearing is Db, the eccentric part it is a diameter of
Dse, the crankshaft body with a diameter of D at one of cooperation in the base bearing and the supplementary bearingsb, institute
State D, Dro、Dri、e、Db、Dse、Dsb、δminMeet：
|D-Dro-2e-2δmin+0.625(Dri+Db-Dse-Dsb)|≤10μm。
5. rotary compressor according to claim 4, it is characterised in that described D, Dro、Dri、e、Db、Dse、Dsb、δmin
Further meet：
D-Dro-2e-2δmin+0.625(Dri+Db-Dse-Dsb)=0.
6. rotary compressor according to claim 1, it is characterised in that the rotary compressor compresses for single cylinder
Machine.
7. rotary compressor according to claim 1, it is characterised in that the rotary compressor compresses for twin-tub
Machine.
8. rotary compressor according to claim 1, it is characterised in that the rotary compressor compresses for constant speed
Machine.
9. rotary compressor according to claim 1, it is characterised in that the rotary compressor compresses for frequency conversion
Machine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| 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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| Publication Number | Publication Date |
|---|---|
| CN107061273A true CN107061273A (en) | 2017-08-18 |
| CN107061273B CN107061273B (en) | 2019-09-06 |
Family
ID=59619463
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611095257.5A Active CN107061273B (en) | 2016-12-01 | 2016-12-01 | Rotary compressor |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109026698A (en) * | 2018-08-08 | 2018-12-18 | 珠海凌达压缩机有限公司 | A kind of compressor |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN202132234U (en) * | 2011-06-21 | 2012-02-01 | 广东美芝制冷设备有限公司 | Double-slip-sheet type rotary compressor |
| 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 |
-
2016
- 2016-12-01 CN CN201611095257.5A patent/CN107061273B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN102444582A (en) * | 2010-09-30 | 2012-05-09 | 广东美芝制冷设备有限公司 | Rotary type 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 |
| CN202132234U (en) * | 2011-06-21 | 2012-02-01 | 广东美芝制冷设备有限公司 | Double-slip-sheet type rotary 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 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109026698A (en) * | 2018-08-08 | 2018-12-18 | 珠海凌达压缩机有限公司 | A kind of compressor |
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| CN107061273B (en) | 2019-09-06 |
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