CN107091233A

CN107091233A - Rotary compressor

Info

Publication number: CN107091233A
Application number: CN201710526279.0A
Authority: CN
Inventors: 欧智成; 郑礼成
Original assignee: Guangdong Meizhi Compressor Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd
Priority date: 2017-06-30
Filing date: 2017-06-30
Publication date: 2017-08-25
Anticipated expiration: 2037-06-30
Also published as: CN107091233B

Abstract

The invention discloses a kind of rotary compressor, the rotary compressor includes motor component and compression member, and the compression member includes：Bent axle, the bent axle includes axle portion and eccentric part, and the axle portion is connected with the motor component, and one end of the remote motor component of the eccentric part is formed as crankshaft thrust portion；Thrust plate, the thrust plate push stopping part that the thrust plate is formed as coordinating with the crankshaft thrust portion close to one end of the motor component, the thrust plate is provided with the flexible structure for the axial stiffness for being used to reduce the thrust plate push stopping part.Rotary compressor according to embodiments of the present invention can reduce the frictional dissipation of thrust friction pair, extend the service life of compressor, improve the compression efficiency of compressor.

Description

Rotary compressor

Technical field

The present invention relates to refrigeration technology field, in particular to a kind of rotary compressor.

Background technology

In correlation technique, rotor type rotary compressor is generally stopped using the lower surface in the countershaft portion of bent axle as bent axle Pushed section, coordinates with the pushing surface of thrust plate and slides thrust friction pair to be formed, so as to limit the axial movement of bent axle in good time.

Find in actual use, the abrasion of the thrust friction pair of said structure is very serious, has a strong impact on compressor Performance, especially this shortcoming is especially prominent under severe operating condition.

The content of the invention

It is contemplated that at least solving one of technical problem present in prior art.Therefore, the present invention proposes a kind of energy Enough reduce the rotary compressor of thrust frictional dissipation.

Rotary compressor according to embodiments of the present invention includes motor component and compression member, the compression member bag Include：Bent axle, the bent axle includes axle portion and eccentric part, and the axle portion is connected with the motor component, the eccentric part it is remote One end of the motor component is formed as crankshaft thrust portion；Thrust plate, one end shape of the thrust plate close to the motor component As the thrust plate push stopping part coordinated with the crankshaft thrust portion, the thrust plate, which is provided with, to be used to reduce the thrust plate push stopping part Axial stiffness flexible structure.

Rotary compressor according to embodiments of the present invention, by setting flexible structure on thrust plate to reduce thrust plate The rigidity of push stopping part partly or wholly in the axial direction, bent axle is under external applied load (based on gas force Fg) effect during work, only Push pedal push stopping part can partly or wholly produce moderate finite deformation in the axial direction, so that thrust plate push stopping part is filled with crankshaft thrust portion Tap is touched, and makes the distribution of contact acted on thrust friction pair evenly, and then effectively reduce the mill of thrust friction pair Damage, simultaneously because reducing the area of Rough Contact, therefore also effectively reduce friction loss, extend the use longevity of compressor Life, improves the compression efficiency of compressor.

According to some embodiments of the present invention, the flexible structure is flexible slot.

According to some embodiments of the present invention, the crankshaft thrust portion is radially towards the central axis side away from the axle portion To moving closer to the motor component.

According to some embodiments of the present invention, the crankshaft thrust portion and the plane of the central axis perpendicular to the axle portion Angle theta≤1 °.

According to some embodiments of the present invention, the flexible slot be disposed radially and with the thrust plate push stopping part interval Open, wherein, radially refer to perpendicular to axially direction, be axially the central axial direction of the axle portion.

According to some embodiments of the present invention, the top of the flexible slot is extended radially through in the thrust plate along described Wall.

According to some embodiments of the present invention, the bottom wall of the flexible slot is circular arc, the center of curvature of the bottom wall with The central axis of the axle portion is conllinear.

According to some embodiments of the present invention, the thickness between the inwall of the flexible slot and the thrust plate push stopping part is The wall thickness of the flexible slot, the wall thickness of the flexible slot diametrically towards on the direction of the central axis away from the axle portion gradually The wall thickness for reducing increase or the flexible slot is steady state value.

According to some embodiments of the present invention, the angle α between the side wall and thrust plate push stopping part of the flexible slot is met Relation：0≤α≤20°

According to some embodiments of the present invention, the width of the flexible slot in the axial direction is steady state value.

According to some embodiments of the present invention, the flexible slot is in the depth capacity H radially and the flexible slot Average wall thickness T ratio meet following condition：1≤H/T≤10.

According to some embodiments of the present invention, the flexible slot is in the depth capacity H >=2mm radially.

According to some embodiments of the present invention, average wall thickness T >=1mm of the flexible slot.

According to some embodiments of the present invention, minimum widith W >=1mm of the flexible slot on the axial direction.

According to some embodiments of the present invention, the rotary compressor is single cylinder compressor, and the compression member includes pair Bearing, the supplementary bearing is formed as the thrust plate.

According to some embodiments of the present invention, the rotary compressor is multicylinder compressor, and the eccentric part is multiple, institute Stating compression member includes supplementary bearing and the median septum being disposed between adjacent eccentric portion, the supplementary bearing or the median septum Be formed as the thrust plate.

According to some embodiments of the present invention, the rotary compressor is vertical rotating formula compressor or horizontal rotary 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 schematic diagram of traditional rotary compressor,

Fig. 2 is the stress diagram of the thrust friction pair of traditional rotary compressor.

Fig. 3 is the schematic diagram of rotary compressor according to an embodiment of the invention.

Fig. 4 is the stress diagram of the thrust friction pair of rotary compressor according to an embodiment of the invention.

Fig. 5 is the schematic top plan view of the bent axle of rotary compressor according to an embodiment of the invention.

Fig. 6 is the schematic cross-sectional view of the bent axle of rotary compressor according to an embodiment of the invention.

Fig. 7 is the Max.contact stress of rotary compressor according to an embodiment of the invention and H/T curved line relation Schematic diagram.

Fig. 8 is that (compressor is for the elevational schematic view of the bent axle of the rotary compressor according to another of the invention embodiment During single cylinder).

Reference：

Traditional structure：

Bent axle 10 ', main shaft part 11 ', countershaft portion 12 ', eccentric part 13 ', crankshaft thrust portion 14 ', base bearing 30 ', supplementary bearing 40 ', piston 50 ', cylinder 60 ',

The application：

Rotary compressor 100, bent axle 10, main shaft part 11, countershaft portion 12, eccentric part 13, upper eccentric part 131, lower bias Portion 132, crankshaft thrust portion 14,

Flexible slot 20, the bottom wall 21 of flexible slot,

Base bearing 30,

Supplementary bearing 40,

Piston 50, upper piston 51, lower piston 52,

Cylinder 60, upper cylinder 61, lower cylinder 62,

Median septum 70,

Thrust plate push stopping part 81.

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.

The application is applicant based on the recognition that making：

Structure description to traditional rotary compressor is as follows：Shown in reference picture 1, traditional rotary compressor includes Motor component and compression member, compression member include：Cylinder 60 ', piston 50 ', slide plate (not shown), base bearing 30 ', pair Bearing 40 ' and bent axle 10 ' etc..Suction muffler and discharge chamber, the axle portion that motor component passes through bent axle 10 ' are separated into cylinder 60 ' Compression member motion is driven, is changed with the volume for realizing suction muffler and discharge chamber, to complete constantly suction, compression and discharge refrigerant The course of work.

Bent axle 10 ' includes axle portion and eccentric part 13 ', and axle portion includes main shaft part 11 ' and countershaft portion 12 ', main shaft part 11 ' and master Bearing 30 ' is connected with merging with motor component, and countershaft portion 12 ' coordinates with supplementary bearing 40 '.Bent axle 10 ' is remote by countershaft portion 12 ' One end (countershaft end) of motor component is crankshaft thrust portion 14 ', and thrust plate is thrust plate close to the surface of the side of motor component Push stopping part, the plate body that thrust plate can be supplementary bearing 40 ' or median septum or only be against below supplementary bearing 40 '.Thrust plate Push stopping part coordinates with crankshaft thrust portion 14 ', and then limits the axial movement of bent axle 10 '.Crankshaft thrust portion 14 ' and thrust plate thrust Portion collectively forms slip thrust friction pair.The oil sump of compressor is rubbed by the oil feeding line (not shown) of bent axle 10 ' to thrust Wipe secondary fuel feeding and lubrication.

For existing rotary compressor, the serious wear of thrust friction vice division chief, especially in badly operation work This phenomenon is especially prominent under condition.So, not only the reliability of compressor operating is poor, and needs often to change parts, Larger friction loss is caused simultaneously, the performance of compressor is had a strong impact on.

For existing design thrust friction pair wear reason, those skilled in the art can not fundamentally recognize make always Into the key factor of abrasion.In consideration of it, the applicant through largely, repeatedly, in depth research just find and specify that to cause thrust Friction pair weares and teares the key factor of this problem.Fig. 2 is the explanation that the applicant studies the thrust friction pair abrasion principle found Figure.For convenience of observing, the deformation of bent axle 10 ' is exaggerated in figure.

Applicants have discovered that, bent axle 10 ' is acted on by axial force F m, and axial force F m mainly includes rotatable parts itself institute By gravity and motor axial magnetic pull.And the eccentric part 13 ' of bent axle 10 ' is in the gas caused by suction muffler and compression chamber pressure difference In the presence of power Fg, bent axle 10 ' is set to generate moderate finite deformation, as shown in Figure 2.

Crankshaft thrust portion 14 ' is by run-off the straight after bent axle 10 ' is deformed, outside and the supplementary bearing 40 ' in crankshaft thrust portion 14 ' End face formation linear contact lay, and then result in localized contact stress concentration, figure to thrust friction pair contact stress P distribution carry out Signal.So, excessive localized contact stress will cause violent abrasion, push stopping part scratch or adhesion be even resulted in, when serious The failure of thrust friction pair can be caused.

As can be seen here, bent axle 10 ' deforms the key factor for being only and causing thrust friction pair to wear and tear caused by gas force Fg.

The applicant further study show that, led because gas force is main by operating condition and the diameter of cylinder 60 ', height etc. Structural parameters are wanted to determine, and the diameter of axle of bent axle 10 ', generally using pathization design, is led for the consideration of lifting compressor performance Cause the rigidity of bent axle 10 ' poor, finally cause the problem of abrasion of thrust friction pair turns into more universal in the industry.Also just because of gas force Fg and the rigidity of bent axle 10 ' are restricted by other factors, are difficult to change, so making the improvement that thrust friction pair weares and teares by very big system About, with larger difficulty.

The present invention is had found based on the studies above, creatively proposes and flexible structure is set near thrust plate push stopping part Solution, is not only simple in structure, conveniently implements, and improvement is extremely notable.

Rotary compressor 100 according to embodiments of the present invention is described in detail below with reference to Fig. 3 to Fig. 8.

As shown in figure 3, rotary compressor 100 according to embodiments of the present invention includes motor component and compression member, Compression member includes：Bent axle 10 and thrust plate, bent axle 10 include axle portion and eccentric part 13, and axle portion is connected with motor component, eccentric One end of the remote motor component in portion 13 is formed as crankshaft thrust portion 14, and thrust plate is formed as close to one end of the motor component The thrust plate push stopping part coordinated with the crankshaft thrust portion 14.

Wherein, thrust plate is provided with the flexible structure for the axial stiffness for being used to reduce the thrust plate push stopping part.

Rotary compressor 100 according to embodiments of the present invention, by setting flexible structure on thrust plate to reduce only The rigidity of push pedal push stopping part partly or wholly in the axial direction, bent axle 10 is acted in external applied load (based on gas force Fg) during work Under, thrust plate push stopping part can partly or wholly produce moderate finite deformation in the axial direction, so that thrust plate push stopping part is stopped with bent axle Pushed section is fully contacted, and makes the distribution of contact acted on thrust friction pair evenly, and then effectively reduces thrust friction Secondary abrasion, simultaneously because reducing the area of Rough Contact, therefore also effectively reduces friction loss, extends compressor Service life, improves the compression efficiency of compressor.

It is appreciated that compression member includes：Cylinder 60, piston 50, slide plate (not shown), base bearing 30, supplementary bearing 40 and bent axle 10 etc..Suction muffler and discharge chamber are separated into cylinder 60, motor component is driven by the axle portion of bent axle 10 to be compressed Part is moved, and is changed with the volume for realizing suction muffler and discharge chamber, to complete the worked of constantly suction, compression and discharge refrigerant Journey.

The axle portion of bent axle 10 includes main shaft part 11 and countershaft portion 12, and main shaft part 11 is matched somebody with somebody with base bearing 30 and merged and motor component Connection, countershaft portion 12 coordinates with supplementary bearing 40, and thrust plate can be stopped by muffler to be against on supplementary bearing 40 and bent axle 10, only Push pedal can also directly be connected with supplementary bearing 40 and only be against on bent axle 10, and thrust plate can also be formed as supplementary bearing.Thrust plate Push stopping part is only supported with the crankshaft thrust portion 14 on eccentric part 13 to be coordinated.

Rotary compressor 100 shown in Fig. 3 to Fig. 8 is single cylinder rotary compressor, and compression member includes supplementary bearing 40, Supplementary bearing 40 is formed as thrust plate.It is appreciated that above-described embodiment is equally applicable to multi-cylinder rotary compressor.For multi-cylinder pressure For contracting machine, eccentric part is multiple, and compression member includes supplementary bearing 40 and the median septum being disposed between adjacent eccentric portion, Supplementary bearing 40 or median septum are formed as thrust plate.

As shown in figure 4, rotary compressor 100 according to an embodiment of the invention, flexible structure is flexible slot 20.By This, by setting flexible slot 20 in the countershaft portion 12 of bent axle 10, so that the rigidity of thrust plate push stopping part 81 in the axial direction is significantly Reduction, so when bent axle 10 is in gas force F_gWhen being deformed under effect, crankshaft thrust portion 14 still can be with the end face of supplementary bearing 40 Preferably retaining surface is contacted, and then makes the contact stress acted on thrust friction pair more uniform, significantly reduces maximum Contact stress and Rough Contact degree, so as to improve the abrasion and friction loss of thrust friction pair.

Certainly, flexible structure is not limited to flexible slot 20, it would however also be possible to employ inlay elasticity in thrust plate push stopping part 81 The modes such as the less material of modulus are to reduce the axial rigidity of thrust plate push stopping part 81, that is to say, that those skilled in the art can Rigid other knots on thrust plate of thrust plate push stopping part 81 partly or wholly in the axial direction can be reduced with what is expected Structure is also covered by the application protection domain, numerous to list herein.

The applicant it has been investigated that, due near thrust plate push stopping part 81 be provided with flexible slot 20, thrust plate thrust Portion 81 gradually increases towards rigidity on the direction away from the axle portion axis of bent axle 10, and bent axle 10 deforms under gas force effect When, the outside of thrust plate push stopping part 81 carries larger (as shown in Figure 2), can so cause the contact to acting on supporting leg friction vice division chief The improvement of stress is not good, it is therefore desirable to be obliquely installed crankshaft thrust portion 14.

Such as Fig. 5, crankshaft thrust portion 14 is spaced apart with thrust plate push stopping part 81, and crankshaft thrust portion 14 is radially towards away from axle portion Central axial direction move closer to motor component.So, the load for acting on the inner side of thrust plate push stopping part 81 can be increased, together Shi Youxiao plays the effect of flexible slot 20.

The size deformed in view of the eccentric part 13 of bent axle 10 under gas force effect, the angle of inclination of crankshaft thrust portion 14 is unsuitable It is excessive, crankshaft thrust portion 14 and angle theta≤1 ° of the plane of the central axis perpendicular to axle portion.

For the ease of fabricating and being formed non-uniform wall thickness, the upper lower wall surface and the thrust plate of thrust plate of flexible slot 20 Push stopping part 81 is non-parallel, that is, is formed and tilt flexible slot.Specifically, as shown in Fig. 8 (Fig. 7), the side wall of flexible slot 20 radially towards Central axial direction away from thrust plate is gradually distance from thrust plate push stopping part 81.Further, the side wall of flexible slot 20 and thrust Angle α between plate push stopping part 81 meets relation：0≤α≤20°

According to some embodiments of the present invention, flexible slot 20 is disposed radially and is spaced apart with thrust plate push stopping part, wherein, Radially refer to perpendicular to axially direction, be axially the central axial direction of the axle portion 12 of bent axle 10.So, it will not only destroy Thrust plate push stopping part 81, and enable crankshaft thrust portion 14 gas force effect under be directed away from motor component direction move It is dynamic, and then crankshaft thrust portion 14 is fully contacted with corresponding thrust plate push stopping part 81, so thrust rub vice division chief's formation compared with Good hydrldynamic pressure lubrication, reduces abrasion, enhances the stability and reliability of compressor operating.

Preferably, as shown in Figure 4 and Figure 5, the top of flexible slot 20 extends radially through the inwall of thrust plate. In other words, the notch formation of flexible slot 20 is on the inwall of thrust plate.So, it is more convenient processing.

It is appreciated that the top of flexible slot 20 can also be not through thrust plate lateral wall or the top of flexible slot 20 A part runs through the lateral wall of thrust plate.

In the specific embodiment shown in Fig. 5, the bottom wall 21 of flexible slot 20 can be circular arc, the center of curvature of bottom wall 21 It is conllinear with the central axis of the axle portion of bent axle 10.That is, flexible slot can be annular groove.

Further study show that, the size design of flexible slot 20 influences very big for improvement.As shown in Figure 6 and Figure 7, The radial direction depth capacity H of flexible slot 20 and average wall thickness T ratios affect is the most key, with H/T increase, thrust plate push stopping part 81 rigidity is gradually reduced, Max.contact stress P_maxIt is rapid to reduce；But with H/T further increase, thrust plate push stopping part 81 Rigidity it is too small when, the integrated distribution of contact stress can be caused again, makes Max.contact stress P_maxIncrease.

According to above-mentioned theory and correlation test research find, flexible slot 20 the depth capacity H radially with it is described The average wall thickness T of flexible slot 20 ratio meets following condition：Improvement is preferable during 1≤H/T≤10.Wherein, flexible slot 20 Inwall and the thrust plate push stopping part 81 between thickness be the flexible slot 20 wall thickness, average wall thickness T=flexible slots 20 The projected area S of the volume V/ flexible slots 20 of inwall between inwall and thrust plate push stopping part vertically.

Advantageously, the depth capacity H >=2mm of flexible slot 20 diametrically.That is, flexible slot 20 is along in axle portion Depth capacity H >=2mm of radial direction centered on heart axis.

The size design of flexible slot 20 is unfavorable for processing and manufacturing when too small, in order to improve processing technology, can use as follows Design：Average wall thickness T >=1mm of flexible slot 20, the minimum widith W >=1mm of flexible slot 20 in the axial direction.In the tool shown in Fig. 6 In body embodiment, it is gradually reduced radially towards the direction of the axis of the axle portion away from bent axle 10, now W is minimum width value.

For convenience of fabricating, the width of flexible slot 20 in the axial direction can also be steady state value, and now minimum widith W is exactly The fixation groove width of flexible slot 20.

In the specific embodiment shown in Fig. 3 to Fig. 7, the thickness between the inwall and thrust plate push stopping part 81 of flexible slot 20 For the wall thickness of flexible slot 20, the wall thickness of flexible slot 20 is diametrically towards being gradually reduced on the direction of the central axis away from axle portion.

Certainly, the present invention is not limited thereto, and the wall thickness of flexible slot 20 can have multiple choices, in the specific reality shown in Fig. 5 Apply in example, the wall thickness of flexible slot 20 is steady state value.Using etc. wall thickness flexible slot 20 design, increase is reduced to greatest extent flexible The influence that groove 20 is processed to bent axle 10, processing technology is more preferable.

In addition, the restriction of above-mentioned size (such as H, T, W) for flexible slot 20 etc. is for the specific reality shown in Fig. 7 to Fig. 8 Apply example to be also suitable, will not be described here.In the specific embodiment shown in Fig. 7, the wall thickness of flexible slot 20 is steady state value, therefore averagely Thickness between the inwall and thrust plate push stopping part 81 of wall thickness T=flexible slots 20 is the wall thickness of flexible slot 20.

The present invention program is equally applicable to multicylinder compressor, and application of the present invention on duplex cylinder compressor is illustrated. The number of the eccentric part 13 of multicylinder compressor is multiple, and one end of the remote motor component of eccentric part 13 is formed as crankshaft thrust portion 14, flexible structure is arranged on thrust plate, and now any one in median septum and supplementary bearing can be formed as thrust plate.

For example, in the specific embodiment shown in Fig. 8, multicylinder compressor includes upper cylinder 61, lower cylinder 62, upper work Plug 51, lower piston 52, the upper eccentric part 131 of bent axle 10 is located in upper cylinder 61 and upper piston 51 is connected with upper eccentric part 131, bent The lower eccentric part 132 of axle 10 is connected positioned at 52 times eccentric parts of lower cylinder 62 and lower piston 132.Compressor be located at upper eccentric part under The median septum 70 of side is formed as thrust plate, crankshaft thrust portion 14 and the thrust plate push stopping part formation thrust friction pair of median septum 70, Flexible slot 20 is formed on median septum.For the consideration of assembling, median septum can be designed as split type, i.e., median septum is in figure Two median septums 70 are combined.

In addition, the rotary compressor can be vertical rotating formula compressor or horizontal rotary compressor.Above-mentioned thrust Where plate push stopping part, crankshaft thrust portion 14, median septum push stopping part, supplementary bearing push stopping part etc. can be formed in each on part Thrust surface.

In the description of the invention, it is to be understood that term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", " under ", "front", "rear", "left", "right", " vertical ", " level ", " top ", " bottom " " interior ", " outer ", " up time The orientation or position relationship of the instruction such as pin ", " counterclockwise ", " axial direction ", " radial direction ", " circumference " be based on orientation shown in the drawings or Position relationship, is for only for ease of the description present invention and simplifies description, rather than indicate or imply that the structure or element of meaning must There must be specific orientation, with specific azimuth configuration and operation, therefore be not considered as limiting the invention.In addition, limit Surely there is " first ", one or more this feature can be expressed or be implicitly included to the feature of " second ".The present invention's In description, unless otherwise indicated, " multiple " are meant that two or more.

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

1. a kind of rotary compressor, it is characterised in that including motor component and compression member, the compression member includes：

Bent axle, the bent axle includes axle portion and eccentric part, and the axle portion is connected with the motor component, the eccentric part it is remote One end of the motor component is formed as crankshaft thrust portion；

Thrust plate, the thrust plate that the thrust plate is formed as coordinating with the crankshaft thrust portion close to one end of the motor component Push stopping part, the thrust plate is provided with the flexible structure for the axial stiffness for being used to reduce the thrust plate push stopping part.

2. rotary compressor according to claim 1, it is characterised in that the flexible structure is flexible slot.

3. rotary compressor according to claim 2, it is characterised in that the crankshaft thrust portion is radially towards away from institute The central axial direction for stating axle portion moves closer to the motor component.

4. rotary compressor according to claim 3, it is characterised in that the crankshaft thrust portion with perpendicular to the axle Angle theta≤1 ° of the plane of the central axis in portion.

5. rotary compressor according to claim 3, it is characterised in that the flexible slot be disposed radially and with it is described Thrust plate push stopping part is spaced apart, wherein, radially refer to perpendicular to axially direction, be axially the central axis side of the axle portion To.

6. rotary compressor according to claim 3, it is characterised in that the top of the flexible slot is passed through along the radial direction Wear the inwall of the thrust plate.

7. rotary compressor according to claim 3, it is characterised in that the bottom wall of the flexible slot is circular arc, institute The center of curvature for stating bottom wall is conllinear with the central axis of the axle portion.

8. rotary compressor according to claim 3, it is characterised in that the inwall of the flexible slot and the thrust plate Thickness between push stopping part is the wall thickness of the flexible slot, and the wall thickness of the flexible slot is diametrically towards away from the axle portion Gradually the wall thickness of increase or the flexible slot is steady state value on the direction of heart axis.

9. rotary compressor according to claim 8, it is characterised in that the side wall of the flexible slot and thrust plate thrust Angle α between portion meets relation：0≤α≤20°.

10. rotary compressor according to claim 3, it is characterised in that the width of the flexible slot in the axial direction is Steady state value.

11. the rotary compressor according to any one of claim 3-10, it is characterised in that the flexible slot is described Depth capacity H radially and the average wall thickness T of the flexible slot ratio meet following condition：1≤H/T≤10.

12. the rotary compressor according to any one of claim 3-10, it is characterised in that the flexible slot is in institute State depth capacity H >=2mm radially.

13. the rotary compressor according to any one of claim 3-10, it is characterised in that the flexible slot is averaged Wall thickness T >=1mm.

14. the rotary compressor according to any one of claim 3-10, it is characterised in that the flexible slot is described Minimum widith W >=1mm on axial direction.

15. rotary compressor according to claim 2, it is characterised in that the rotary compressor is single cylinder compressor, The compression member includes supplementary bearing, and the supplementary bearing is formed as the thrust plate.

16. rotary compressor according to claim 2, it is characterised in that the rotary compressor is multicylinder compressor, The eccentric part is multiple, and the compression member includes supplementary bearing and the median septum being disposed between adjacent eccentric portion, institute State supplementary bearing or the median septum is formed as the thrust plate.

17. rotary compressor according to claim 1, it is characterised in that the rotary compressor is vertical rotating Formula compressor or horizontal rotary compressor.