CN214698344U

CN214698344U - Scroll compressor and air conditioner

Info

Publication number: CN214698344U
Application number: CN202120907175.6U
Authority: CN
Inventors: 罗承卓; 谭琴; 宋红飞
Original assignee: Guangdong Midea Environmental Technologies Co Ltd
Current assignee: Guangdong Midea Environmental Technologies Co Ltd
Priority date: 2021-04-28
Filing date: 2021-04-28
Publication date: 2021-11-12
Anticipated expiration: 2031-04-28

Abstract

The utility model discloses a scroll compressor and an air conditioner, wherein the scroll compressor comprises a shell, a compression assembly and a motor, the compression assembly comprises a main frame, a movable disc and a static disc, and the main frame is provided with a first supporting part and a groove; the movable disc is arranged on the main frame, and one end of the movable disc is provided with a second supporting part; the motor is provided with a crankshaft, a central oil hole is formed in the crankshaft, the crankshaft comprises a long shaft and an eccentric shaft, the long shaft penetrates through the first supporting part, the outer peripheral wall of the long shaft is provided with an oil outlet and a first oil groove communicated with the oil outlet and the groove, and the oil outlet and the first oil groove are formed in a matching area of the long shaft and the first supporting part; the eccentric shaft penetrates through the second supporting part, and the peripheral wall of the eccentric shaft is provided with a second oil groove communicated with the first oil groove. The utility model discloses an oil outlet and first oil groove guide lubricating oil are lubricated to the cooperation department between first bearing part and the major axis, and through the second oil groove guide lubricating oil to the cooperation department lubrication of second bearing part and eccentric shaft, the reliability of bent axle and supporting part has been improved.

Description

Scroll compressor and air conditioner

Technical Field

The utility model relates to a compressor technical field, in particular to scroll compressor and air conditioner.

Background

In the related art, for the scroll compressor with high back pressure, because the compression cavity is arranged above the shell and is far away from the oil pool, oil supply of the compression cavity and bearing lubrication oil supply are difficult problems in the industry all the time, and common oil supply modes comprise gear pump oil supply, eccentric oil supply, differential pressure oil supply and the like. The method for differential pressure oil supply has wide applicability and low cost, but the key of the differential pressure oil supply is to form differential pressure, so that the problem of insufficient oil supply quantity when the differential pressure is small exists, the oil supply of a bearing lubricating system is insufficient, and the reliability of a crankshaft and a bearing is influenced.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, the utility model provides a scroll compressor can solve the not enough problem of bearing lubrication system fuel feeding that the scroll compressor pressure differential oil feeding mode exists.

The utility model also provides an air conditioner of having above-mentioned scroll compressor.

According to the utility model discloses compression assembly of first aspect embodiment includes: a housing having a lubricant therein; the compression assembly is arranged in the shell and comprises a main frame, a movable disc and a static disc; the main frame is provided with a first supporting part and a groove; the movable disc is arranged on the main rack, one end of the movable disc is provided with a second supporting part, the second supporting part is positioned in the groove, and the static disc is meshed with the other end of the movable disc to form a compression cavity; a motor disposed in the housing and having a crankshaft; a central oil hole is formed in the crankshaft, the central oil hole is used for allowing the lubricating oil to flow into the compression assembly from the interior of the shell, the crankshaft comprises a long shaft and an eccentric shaft, the long shaft penetrates through the first supporting part, an oil outlet hole and a first oil groove are formed in the peripheral wall of the long shaft, the oil outlet hole is communicated with the central oil hole, the first oil groove is communicated with the oil outlet hole and extends towards the direction of the eccentric shaft, the first oil groove is communicated with the groove, and the oil outlet hole and the first oil groove are formed in a matching area of the long shaft and the first supporting part; the eccentric shaft penetrates through the second supporting part, a second oil groove is formed in the peripheral wall of the eccentric shaft, is formed in one end face, away from the long shaft, of the eccentric shaft and extends towards the direction of the long shaft, and the second oil groove is communicated with the groove.

According to the utility model discloses compression assembly has following beneficial effect at least:

by arranging the crankshaft with the central oil hole, the crankshaft comprises a long shaft which is in running fit with the main frame and an eccentric shaft which is in running fit with the movable disc, the peripheral wall of the long shaft is provided with an oil outlet hole and a first oil groove which extends along the direction of the eccentric shaft, the first oil groove is communicated with the groove, the peripheral wall of the eccentric shaft is provided with a second oil groove which extends along the direction of the long shaft, the second oil groove is communicated with the groove, the scroll compressor guides the lubricating oil in the shell to the groove through the central oil hole and guides the lubricating oil to lubricate the matching area between the first supporting part of the main frame and the long shaft of the crankshaft when lubricating the compression assembly, and guides the lubricating oil to lubricate the matching area between the second supporting part of the movable disc and the eccentric shaft of the crankshaft through the second oil groove, so that the lubricating oil is guided to the load area of the crankshaft, and the problem of insufficient oil supply of a supporting part lubricating system is solved, the reliability of the crankshaft and the supporting part is improved, and the operation stability of the scroll compressor is improved.

According to some embodiments of the utility model, the inside first pressure chamber that forms of casing, the internal perisporium of main frame with form the second pressure chamber between the periphery wall of driving disk, the pressure of first pressure chamber is greater than the pressure of second pressure chamber, scroll compressor passes through first pressure chamber with the oil supply is realized to the pressure differential of second pressure chamber.

According to the utility model discloses a some embodiments in the axial of major axis, the oil outlet with the cooperation is regional to be kept away from the minimum distance of the one end of eccentric shaft is L, and satisfies: l is more than or equal to 2 mm.

According to some embodiments of the present invention, the cross-sectional area of the first oil groove is S1, and satisfies: s1 is more than or equal to 1mm²(ii) a The cross-sectional area of the second oil groove is S2, and satisfies: s2 is more than or equal to 1mm²。

According to some embodiments of the invention, the first oil groove extends in the axial direction of the long shaft, and the second oil groove extends in the axial direction of the eccentric shaft; on a projection plane perpendicular to the axial direction of the long shaft, a straight line on which a connecting line of the circle center of the long shaft projection and the circle center of the eccentric shaft projection of a coordinate system is located is defined as a y-axis, a straight line passing through the circle center of the long shaft projection and perpendicular to the y-axis is an x-axis, a zero angle is a direction in which the y-axis faces the circle center of the eccentric shaft projection, the clockwise direction is an angle increasing direction, the projection of the first oil groove is located within a range of 0 +/-15 degrees, and the projection of the second oil groove is located within a range of 180 +/-15 degrees.

According to some embodiments of the present invention, the first oil groove is helical, and the second oil groove is helical and has a direction of rotation opposite to the first oil groove; when the crankshaft rotates, the oil in the first oil groove flows towards the direction of the eccentric shaft, and the oil in the second oil groove flows towards the direction of the long shaft.

According to some embodiments of the present invention, the diameter of the long shaft is d1, the pitch of the first oil groove is m1, and satisfies: m1/d1 is more than or equal to 5 and less than or equal to 10; the shaft diameter of the eccentric shaft is d2, the screw pitch of the second oil groove is m2, and the requirements are that: m2/d2 is more than or equal to 5 and less than or equal to 10.

According to some embodiments of the present invention, the second oil groove is spiral, and on the projection plane perpendicular to the axial direction of the long axis, the straight line where the line connecting the center of circle of the long axis projection and the center of circle of the eccentric shaft projection of the coordinate system is located is the y axis, the straight line passing through the center of circle of the long axis projection and perpendicular to the y axis is the x axis, the zero angle is the direction in which the y axis faces the center of circle of the eccentric shaft projection, and the clockwise direction is the direction in which the angle increases; when the rotation direction of the crankshaft is clockwise, the projection of the second oil groove is not in the range of 0-145 degrees; when the rotation direction of the crankshaft is anticlockwise, the projection of the second oil groove is not in the range of 180-325 degrees.

According to the utility model discloses a some embodiments, the major axis is equipped with a plurality ofly the oil outlet, first oil groove intercommunication is a plurality of the oil outlet.

According to the utility model discloses a some embodiments, the major axis is equipped with a plurality ofly oil outlet and a plurality of first oil groove, first oil groove with the oil outlet one-to-one intercommunication.

According to the utility model discloses a some embodiments, the periphery wall of major axis is equipped with first annular, the oil outlet is located in the first annular, first oil groove with first annular intercommunication.

According to the utility model discloses a some embodiments, the internal perisporium of first supporting part is equipped with the second annular, the oil outlet is located the notch department of second annular, first oil groove with second annular intercommunication.

According to some embodiments of the present invention, the diameter of the long shaft is d1, and satisfies: d1 is less than or equal to 18 mm.

According to some embodiments of the present invention, the scroll compressor has a displacement of V, and satisfies: v is less than or equal to 18cm³。

According to the second aspect of the present invention, the air conditioner comprises the scroll compressor of the above embodiments.

According to the utility model discloses air conditioner has following beneficial effect at least:

by adopting the scroll compressor of the first aspect, the scroll compressor is provided with the crankshaft with the central oil hole, the crankshaft comprises the long shaft which is in running fit with the main frame and the eccentric shaft which is in running fit with the movable disc, the peripheral wall of the long shaft is provided with the oil outlet hole and the first oil groove which extends along the direction of the eccentric shaft, the peripheral wall of the eccentric shaft is provided with the second oil groove which extends along the direction of the long shaft and is communicated with the groove, the scroll compressor guides the lubricating oil in the shell to the groove through the central oil hole and guides the lubricating oil to lubricate the matching area between the first supporting part of the main frame and the long shaft of the crankshaft when lubricating the compression assembly, and guides the lubricating oil to lubricate the matching area between the second supporting part of the movable disc and the eccentric shaft of the crankshaft through the second oil groove, thereby guiding the lubricating oil to the load area of the crankshaft, the problem of support part lubricating system fuel feeding not enough is solved, the reliability of bent axle and support part has been improved, scroll compressor's operating stability has been promoted, and then the operating stability of air conditioner has been promoted.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

The invention will be further described with reference to the following drawings and examples, in which:

fig. 1 is a schematic structural view of a scroll compressor according to an embodiment of the present invention;

FIG. 2 is an enlarged view taken at A in FIG. 1;

fig. 3 is an enlarged schematic view of a main frame and a crankshaft of a scroll compressor according to an embodiment of the present invention;

FIG. 4 is a schematic structural view of a movable platen of a scroll compressor according to an embodiment of the present invention;

fig. 5 is a schematic structural view of a stationary plate of a scroll compressor according to an embodiment of the present invention;

FIG. 6 is a schematic cross-sectional view of a crankshaft of a scroll compressor according to an embodiment of the present invention;

FIG. 7 is a front view of FIG. 6;

FIG. 8 is a schematic structural view of a crankshaft of a scroll compressor according to another embodiment of the present invention;

FIG. 9 is a schematic cross-sectional view of a crankshaft of a scroll compressor according to another embodiment of the present invention;

FIG. 10 is a front view of FIG. 9;

FIG. 11 is a schematic cross-sectional view of a crankshaft of a scroll compressor according to another embodiment of the present invention;

FIG. 12 is a schematic cross-sectional view of a crankshaft of a scroll compressor according to another embodiment of the present invention;

FIG. 13 is a schematic view of a crankshaft of a scroll compressor according to another embodiment of the present invention;

FIG. 14 is a schematic top view of a crankshaft of a scroll compressor according to another embodiment of the present invention;

FIG. 15 is a schematic top view of a crankshaft of a scroll compressor according to another embodiment of the present invention;

fig. 16 is a schematic top view of a crankshaft of a scroll compressor according to another embodiment of the present invention.

Reference numerals:

a scroll compressor 1000;

a housing 100; an air intake duct 110; an exhaust pipe 120; a base 130; a first pressure chamber 140;

a compression assembly 200; a main frame 210; a first bearing housing 211; a first bearing 212; a recess 213; a movable plate 220; the first scroll portion 221; a second bearing housing 222; a second bearing 223; a stationary disk 230; the second scroll portion 231; a compression chamber 240; a second pressure chamber 250; a third pressure chamber 260;

a motor 300; a stator 310; a rotor 320; a crankshaft 330; a center oil hole 331; an inlet 3311; an outlet 3312; a long axis 332; the first oil outlet hole 3321; a first oil groove 3322; first ring groove 3323; an eccentric shaft 333; second oil groove 3331.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary only for the purpose of explaining the present invention, and should not be construed as limiting the present invention.

In the description of the present invention, it should be understood that the orientation or positional relationship referred to in the description of the orientation, such as the upper and lower directions, is the orientation or positional relationship shown on the drawings, and is only for convenience of description and simplification of description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed in a specific orientation, and be operated, and therefore should not be construed as limiting the present invention.

In the description of the present invention, a plurality means two or more. If the first and second are described for the purpose of distinguishing technical features, they are not to be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.

In the description of the present invention, unless there is an explicit limitation, the words such as setting, installation, connection, etc. should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above words in combination with the specific contents of the technical solution.

Referring to fig. 1, a scroll compressor 1000 according to an embodiment of the present invention is applied to air conditioners such as a wall unit, a cabinet unit, and an air duct unit. The scroll compressor 1000 of the present embodiment includes a housing 100, a compression assembly 200, and a motor 300. The casing 100 is a closed container provided with an air suction pipe 110 and an air discharge pipe 120. The base 130 is provided at the bottom of the housing 100, and the base 130 can fix the scroll compressor 1000, thereby improving the stability of the operation of the scroll compressor 1000. The casing 100 has a lubricating oil therein for lubricating the compression assembly 200, and the lubricating oil may be contained in an oil sump or only in the bottom of the casing 100, i.e. the lubricating oil flows back to the bottom of the casing 100 by gravity.

Referring to fig. 1 and 2, the compression assembly 200 of the present embodiment includes a main frame 210, a movable plate 220, and a stationary plate 230, and the main frame 210 and the stationary plate 230 are fixedly coupled within the casing 100. Referring to fig. 4 and 5, the movable plate 220 includes a first scroll portion 221 facing the stationary plate 230, the stationary plate 230 includes a second scroll portion 231 facing the movable plate 220, and the first and

second scroll portions

221 and 231 are engaged to form a compression chamber 240. The compression chamber 240 changes in volume, shape, etc. with the rotation of the movable disk 220, thereby performing the processes of gas inlet, flow, and pressure discharge. The compression assembly 200 cooperates with the suction pipe 110 and the discharge pipe 120 to perform suction and discharge of the scroll compressor 1000.

Referring to fig. 2 and 3, the main frame 210 of the present embodiment is provided with a first bearing seat 211, the first bearing seat 211 is mounted with a first bearing 212, and the first bearing 212 may be a sliding bearing or a bushing. The first bearing housing 211 may be installed with one or more first bearings 212, and when the first bearing 212 is provided in plurality, the plurality of first bearings 212 are arranged side by side or at intervals along the axial direction of the first bearing housing 211. The main frame 210 has a groove 213, the groove 213 is formed above the first bearing housing 211, and the first bearing housing 211 communicates with the groove 213.

Referring to fig. 2 and 4, the movable plate 220 of the present embodiment is disposed on the main frame 210 and above the first bearing seat 211. The end of the movable plate 220 away from the first scroll part 221 is provided with a second bearing seat 222, the second bearing seat 222 is provided with a second bearing 223, and the second bearing 223 can be a sliding bearing or a bushing. The second bearing seat 222 is located in the groove 213, the second bearing seat 222 rotates in the groove 213, and a third pressure chamber 260 is enclosed between the second bearing seat 222 and the groove 213.

Referring to fig. 3, the motor 300 of the present embodiment includes a stator 310, a rotor 320, and a crankshaft 330, wherein the stator 310 is fixedly coupled to the housing 100, and the rotor 320 is fixedly coupled to the crankshaft 330. The rotor 320 and the stator 310 cooperate to drive the crankshaft 330 in rotation. The crankshaft 330 is provided with a central oil hole 331 therein, and the central oil hole 331 penetrates through the crankshaft 330 in the vertical direction. The central oil hole 331 has an inlet 3311 at a lower end thereof, and the inlet 3311 is directly inserted into the lubricating oil or inserted into the lubricating oil through a guide tube. The upper end of the central oil hole 331 is provided with an outlet 3312, the outlet 3312 is communicated with the compression assembly 200, and the lubricating oil is supplied to the outlet 3312 through the inlet 3311, so that the lubricating oil enters the compression assembly 200 from an oil pool at the bottom of the casing 100 to supply oil to the compression assembly 200. It can be understood that when the scroll compressor 1000 adopts the differential pressure oil supply mode, the pressure chamber formed between the main frame 210 and the movable platen 220 is under the action of the throttling device therein and under the influence of the pressure of the compression chamber 240, the high pressure inside the casing 100 causes the lubricating oil of the oil pool to be pressed into the central oil hole 331 and supply the oil to the compression assembly 200 through the central oil hole 331. Of course, the scroll compressor 1000 may also adopt other oil supply methods, which are not limited in detail herein.

Referring to fig. 2 and 3, the crankshaft 330 of the present embodiment includes a long shaft 332 and eccentric shafts 333, the eccentric shafts 333 being eccentrically disposed with respect to the long shaft 332, the long shaft 332 being located at a lower end, and the eccentric shafts 333 being located at an upper end. The long shaft 332 penetrates through the first bearing seat 211, and the long shaft 332 is rotatably connected with the first bearing 212, so that the stability of rotation between the long shaft 332 and the main frame 210 is ensured. It is understood that the long shaft 332 may also be rotatably coupled to a first support portion having a structure such as a mounting hole formed at the center of the main frame 210. The eccentric shaft 333 is inserted into the second bearing housing 222, and the eccentric shaft 333 is rotatably connected to the second bearing 223, so that the stability of rotation between the eccentric shaft 333 and the movable disk 220 is ensured. It is understood that the eccentric shaft 333 may also rotate the second support portion connected to a mounting hole or the like at an end of the movable disk 220 remote from the first scroll portion 221.

It can be understood that when the scroll compressor 1000 adopts the differential pressure oil supply method, if the pressure difference is small, there is a problem that the oil supply amount is insufficient, i.e., the oil supply amount of the center oil hole 331 is insufficient, and thus the first bearing 212 and the second bearing 223 are insufficiently lubricated, resulting in large wear of the crankshaft 330 and the main frame 210 and the movable disk 220.

Referring to fig. 2 and 5, the outer peripheral wall of the long shaft 332 of the present embodiment is provided with a first oil outlet hole 3321 and a first oil groove 3322. The first oil outlet hole 3321 communicates with the center oil hole 331, and the first oil groove 3322 communicates with the first oil outlet hole 3321 and extends toward the eccentric shaft 333.

The lubricating oil of the central oil hole 331 flows out through the first oil outlet hole 3321 and is guided upward through the first oil groove 3322, thereby lubricating the first bearing housing 211 and the first bearing 212, and improving the lubricating effect of the crankshaft 330 and the first bearing 212. The first oil groove 3322 communicates with the groove 213, and the lubricating oil can be guided to the groove 213 through the first oil groove 3322, thereby ensuring lubrication between the second support and the main frame 210.

The first oil outlet 3321 and the first oil groove 3322 are both disposed in the matching region between the long shaft 332 and the first bearing 212, or in the matching region between the long shaft 332 and the first supporting portion, so as to prevent the first oil outlet 3321 or the first oil groove 3322 from communicating with the inside of the housing 100, thereby reducing the pressure difference due to pressure relief and affecting the oil supply of the scroll compressor 1000.

Referring to fig. 2 and 5, the outer peripheral wall of the eccentric shaft 333 of the present embodiment is provided with a second oil groove 3331, the second oil groove 3331 is formed in an end surface of the eccentric shaft 333 away from the long axis 332, and the second oil groove 3331 extends in a direction toward the long axis 332. A gap is formed between the upper end surface of the eccentric shaft 333 and the second bearing housing 222, and the lubricating oil in the central oil hole 331 flows out from the outlet 3312, is guided to the outer peripheral wall of the eccentric shaft 333 through the gap, and is guided downward through the second oil groove 3331, so that the second bearing 223 of the second bearing housing 222 is lubricated, and the lubricating effect of the crankshaft 330 and the second bearing 223 is improved. The second oil groove 3331 communicates with the groove 213, and the lubricating oil can be guided to the groove 213 through the second oil groove 3331, thereby ensuring lubrication between the second support and the main frame 210.

It can be understood that, when the axial length of the eccentric shaft 333 is large, the outer peripheral wall of the eccentric shaft 333 may also be provided with a second oil outlet (not shown in the drawings), the second oil outlet is communicated with the central oil hole 331, and the second oil outlet is communicated with the second oil groove 3331, so that the lubricating oil of the central oil hole 331 flows out through the second oil outlet and is guided downwards through the second oil groove 3331, thereby lubricating the second bearing seat 222 and the second bearing 223, and further improving the lubricating effect of the crankshaft 330 and the second bearing 223.

The utility model discloses scroll compressor 1000, through the bent axle 330 that sets up the central oilhole 331, bent axle 330 include with main frame 210 normal running fit's major axis 332 and with movable disk 220 normal running fit's eccentric shaft 333, the periphery wall of major axis 332 is equipped with first oil outlet 3321 and the first oil groove 3322 that extends along eccentric shaft 333 direction. The outer peripheral wall of eccentric shaft 333 is provided with second oil groove 3331 extending in the direction of long axis 332. Scroll compressor 1000 leads to recess 213 with the inside lubricating oil of casing 100 through central oilhole 331, and when lubricating compression assembly 200, guide lubricating oil and lubricate the first bearing 212 of main frame 210 through first oil outlet 3321 and first oil groove 3322, guide lubricating oil and lubricate the second bearing 223 of driving disk 220 through second oil groove 3331, thereby lead lubricating oil to the load region of bent axle 330, the problem of the scroll compressor 1000 that adopts pressure differential oil supply mode because pressure differential little leads to bearing lubrication system not enough to supply oil has been solved, the mobility and the lubrication effect of lubricating oil have been improved, bent axle 330 and bearing lubrication system's reliability has been improved, the operating stability of scroll compressor 1000 has been promoted.

In addition, the surface hardness of the crankshaft 330 is designed to be 50HRC or more, so that the crankshaft 330 can have better wear resistance and higher reliability.

Referring to fig. 2, the scroll compressor 1000 of the present embodiment employs a differential pressure oil supply method. The housing 100 forms a first pressure chamber 140 therein, and a second pressure chamber 250 is formed between an inner peripheral wall of the main frame 210 and an outer peripheral wall of the movable plate 220. The third pressure chamber 260 communicates with the second pressure chamber 250, and the throttle device provided before the third pressure chamber 260 and the second pressure chamber 250 affects the pressure of the second pressure chamber 250, and the intake pressure of the compression chamber 240 also affects the pressure of the second pressure chamber 250, so that the pressure of the second pressure chamber 250 is smaller than the pressure of the third pressure chamber 260, and the pressure of the third pressure chamber 260 is the same as the pressure of the first pressure chamber 140. The scroll compressor 1000 thus supplies oil by the pressure differential between the first pressure chamber 140 and the second pressure chamber 250.

It is understood that the first pressure chamber 140 and the third pressure chamber 260 are high pressure spaces, the second pressure chamber 250 is a middle pressure space, and the compression chamber 240 is a low pressure space, and there is no other passage for communicating the first pressure chamber 140, the third pressure chamber 260, and the second pressure chamber 250 except for the first oil groove 3322 of the long shaft 332 and the second oil groove 3331 of the eccentric shaft 333. Lubricating oil in the oil pool is supplied to the third pressure cavity 260 from the central oil hole 331 upwards through the pressure difference between the high-pressure space and the medium-pressure space under the action of the high-pressure space, then is guided to the second pressure cavity 250, lubricating oil is continuously supplied to the compression cavity 240 from the second pressure cavity 250 through the pressure difference between the medium-pressure space and the low-pressure space, and the compression cavity 240 compresses gas and part of lubricating oil into high-pressure gas under the action of the movable disc 220 and the static disc 230 to be discharged, so that the circulation process of pressure difference oil supply is realized. This embodiment can guarantee the pressure differential between first pressure chamber 140, third pressure chamber 260, second pressure chamber 250 and the compression chamber 240, prevents to take place the pressure release for lubricating oil's mobility is stronger, has effectively avoided the not enough condition of compression chamber 240 and bearing oil feed.

Referring to fig. 3, it can be understood that the end of the long shaft 332 and the first bearing 212, which is away from the eccentric shaft 333, is a first end, the minimum distance between the first oil outlet hole 3321 and the first end along the axial direction of the long shaft 332 is L, and it is satisfied that: l is more than or equal to 2 mm. For example, the minimum distance L between the first oil outlet hole 3321 and the first end in the axial direction of the long axis 332 may be set to 2mm, 3mm, 4mm, or the like, and is not particularly limited herein. The utility model discloses scroll compressor 1000, first oil groove 3322 and first oil outlet 3321 all need be located major axis 332 and first bearing 212 cooperation region, and in order to avoid first oil groove 3322 and first oil outlet 3321 to communicate with each other with casing 100 internal environment, avoid first oil groove 3322 and first oil outlet 3321 to communicate with each other with first pressure chamber 140 promptly, scroll compressor 1000 need set up certain distance's confined space.

It can be understood that, since the first oil groove 3322 communicates with the first oil outlet hole 3321 and is supplied with lubricating oil through the first oil outlet hole 3321, the first oil outlet hole 3321 is closer to the lower end of the fitting region of the long shaft 332 and the first bearing 212 than the end of the first oil groove 3322. Therefore, when the minimum distance L between the first oil outlet hole 3321 and the lower end of the matching area between the long shaft 332 and the first bearing 212 satisfies the parameter range, the first oil outlet hole 3321 can be effectively prevented from being communicated with the first pressure chamber 140, and the oil release of the lubricating oil passage is avoided, thereby affecting the oil supply amount of the scroll compressor 1000.

It is understood that when the long shaft 332 is rotatably coupled to the mounting hole of the main frame 210, L is defined as a minimum distance of the first oil outlet hole 3321 from the end of the long shaft 332 and the mounting hole of the main frame 210 away from the eccentric axis 333 in the region where the first oil outlet hole 3321 is fitted. When L is larger than or equal to 2mm, the first oil outlet 3321 can be effectively prevented from being communicated with the first pressure cavity 140, and the pressure relief of a lubricating oil passage is avoided, so that the oil supply quantity of the scroll compressor 1000 is influenced.

Referring to fig. 6, it can be understood that the cross-sectional area of the first oil groove 3322 is S1 and satisfies: s1 is more than or equal to 1mm²。

For example, the cross-sectional area S1 of the first oil groove 3322 may be set to 1mm²，2mm²，3mm²And the like, and are not particularly limited herein.

When the cross-sectional area S1 of first oil groove 3322 satisfies the above parameter range, it is possible to ensure that first oil groove 3322 has a sufficiently large through-flow section, improving the fluidity of the lubricating oil. It can be understood that when the flow cross section of first oil groove 3322 is sufficiently large, the resistance of the lubricating oil flowing through first oil groove 3322 is smaller, and the lubricating oil can be smoothly guided upward to groove 213 through first oil groove 3322 under the force of the differential pressure oil supply, thereby achieving the effect of sufficient lubrication of the first bearing.

Referring to fig. 7, first oil groove 3322 is linear; referring to fig. 8, first oil groove 3322 has a spiral shape. Of course, the first oil groove 3322 may have other shapes, and is not particularly limited herein.

The cross-sectional area of second oil groove 3331 is S2, and satisfies: s2 is more than or equal to 1mm²。

For example, the cross-sectional area S2 of second oil groove 3331 may be set to 1mm²，2mm²，3mm²And the like, and are not particularly limited herein.

When cross-sectional area S2 of second oil groove 3331 satisfies the above parameter range, second oil groove 3331 can be ensured to have a sufficiently large flow cross section, improving the fluidity of the lubricating oil. It can be understood that when the flow cross section of second oil groove 3331 is sufficiently large, the resistance of the lubricating oil flowing through second oil groove 3331 is smaller, and the lubricating oil can be smoothly guided to groove 213 through second oil groove 3331 under the force of the differential pressure oil supply, thereby achieving the effect of sufficient lubrication of the second bearing.

As shown in fig. 7, second oil groove 3331 is linear; referring to fig. 8, second oil groove 3331 has a spiral shape. Of course, second oil groove 3331 may have other shapes, and is not particularly limited herein.

Therefore, it can be understood that first oil groove 3322 and second oil groove 3331 may adopt a straight structure at the same time, or adopt a spiral structure at the same time; first oil groove 3322 and second oil groove 3331 may be linearly and spirally matched, and the specific use manner is not particularly limited herein.

Referring to fig. 8, it can be understood that first oil groove 3322 has a spiral shape and second oil groove 3331 has a spiral shape. The rotation direction of second oil groove 3331 is opposite to the rotation direction of first oil groove 3322.

When the crankshaft 330 rotates, the oil in the first oil groove 3322 flows toward the eccentric shaft 333, that is, after the lubricating oil flows to the first oil groove 3322 through the first oil outlet 3321, under the action of the rotational centrifugal force of the crankshaft 330, the lubricating oil is guided upwards along the spiral first oil groove 3322, and is guided to the second pressure chamber 250, so that the fluidity of the lubricating oil can be increased, the crankshaft 330 and the first bearing 212 are lubricated more sufficiently, the stability of the operation between the long shaft 332 and the main frame 210 is improved, the oil supply of the compression chamber 240 is improved, and the performance of the scroll compressor 1000 is improved. Especially under the low pressure difference working condition, the supply power of the lubricating oil is insufficient, and the fluidity of the lubricating oil can be improved through the guiding of the spiral first oil groove 3322.

Meanwhile, the oil in second oil groove 3331 flows toward the direction of long axis 332, i.e. after the lubricating oil flows to second oil groove 3331 through central oil hole 331, under the action of the centrifugal force generated by rotation of crankshaft 330, the lubricating oil is guided downwards along spiral second oil groove 3331, and guided to second pressure chamber 250, so that crankshaft 330 and second bearing 223 are lubricated more sufficiently, the stability of operation of eccentric shaft 333 and movable disk 220 is improved, the oil supply of compression chamber 240 is improved, and the performance of scroll compressor 1000 is improved. Especially under the low pressure difference working condition, the supply power of the lubricating oil is insufficient, and the fluidity of the lubricating oil can be improved by guiding through the spiral second oil groove 3331.

It can be appreciated that when the rotation direction of scroll compressor 1000 according to the embodiment of the present invention is clockwise, that is, the rotation direction of crankshaft 330 is clockwise (from the top down looking down), second oil groove 3331 is left-handed, and first oil groove 3322 is right-handed. Thus, the above design enables the lubricating oil to be guided to the load region of the crankshaft 330, increasing the oil film thickness in the heavy load region, improving the lubrication of the long shaft 332 and the first bearing 212, and improving the lubrication of the eccentric shaft 333 and the second bearing 223.

It can be understood that when the rotation direction of the scroll compressor 1000 according to the embodiment of the present invention is counterclockwise, that is, the rotation direction of the crankshaft 330 is counterclockwise, the second oil groove 3331 is right-handed, and the first oil groove 3322 is left-handed. Thus, the above design enables the lubricating oil to be guided to the load region of the crankshaft 330, increasing the oil film thickness in the heavy load region, improving the lubrication of the long shaft 332 and the first bearing 212, and improving the lubrication of the eccentric shaft 333 and the second bearing 223.

Referring to fig. 8, it can be understood that first oil groove 3322 has a spiral shape, the axial diameter of long shaft 332 is d1, the pitch of first oil groove 3322 is m1, and: m1/d1 is more than or equal to 5 and less than or equal to 10. When m1/d1 satisfies the above parameter range, the viscous dynamic force of the helical first oil groove 3322 can be ensured without affecting the formation of the oil film in the load region of the long shaft 332. It should be noted that, theoretically, the greater the viscous dynamic force of first oil groove 3322, the better the lubricating oil fluidity, but the greater the viscous dynamic force, the smaller the pitch of spiral first oil groove 3322, and first oil groove 3322 extends to the load region of long axis 332, thereby affecting the formation of the oil film in the load region of long axis 332. Therefore, proper design of the shaft diameter d1 of the long shaft 332 and the pitch m1 of the first oil groove 3322 are key to improving the performance of the scroll compressor 1000.

Referring to fig. 8, it can be understood that the second oil groove 3331 has a spiral shape, the shaft diameter of the eccentric shaft 333 is d2, the pitch of the second oil groove 3331 is m2, and: m2/d2 is more than or equal to 5 and less than or equal to 10. When m2/d2 satisfies the above parameter range, the viscous power of the spiral second oil groove 3331 can be ensured without affecting the formation of the oil film in the load region of the eccentric shaft 333. In theory, the larger the viscous dynamic force of second oil groove 3331, the better the lubricating oil fluidity, but the larger the viscous dynamic force, the smaller the pitch of spiral second oil groove 3331, and second oil groove 3331 extends to the load region of eccentric shaft 333, thereby affecting the formation of oil film in the load region of eccentric shaft 333. Therefore, it is critical to improve the performance of the scroll compressor 1000 to properly design the shaft diameter d2 of the eccentric shaft 333 and the pitch m2 of the second oil groove 3331.

Referring to fig. 9 and 11, it can be understood that the long shaft 332 is provided with a plurality of first oil outlet holes 3321, and the long shaft 332 is further provided with a plurality of first oil grooves 3322, so that oil lubrication between the long shaft 332 and the first bearing 212 can be ensured when the first bearing housing 211 is relatively long, and the reliability of the connection between the long shaft 332 and the first bearing 212 can be improved.

First oil groove 3322 may be linear as shown in fig. 9, and first oil groove 3322 may be spiral as shown in fig. 11. The utility model discloses bent axle 330, first oil groove 3322 and first oil outlet 3321 one-to-one intercommunication, every first oil groove 3322 corresponds a first oil outlet 3321 respectively promptly. Each first oil outlet hole 3321 and each first oil groove 3322 may be respectively disposed corresponding to one first bearing 212, and each first oil outlet hole 3321 guides the lubricating oil to the corresponding first oil groove 3322, so as to ensure lubrication of the long shaft 332 and the first bearing 212, solve the problem of insufficient oil supply of the bearing lubrication system, improve the reliability of the long shaft 332 and the first bearing 212, and improve the operation stability of the scroll compressor 1000.

Referring to fig. 10 and 12, it can be understood that the long shaft 332 is provided with a plurality of first oil outlet holes 3321, and the first oil groove 3322 communicates with the plurality of first oil outlet holes 3321, so that oil lubrication between the long shaft 332 and the first bearing 212 can be ensured when the first bearing housing 211 is relatively long, and the reliability of the connection between the long shaft 332 and the first bearing 212 can be improved. First oil groove 3322 may be linear as shown in fig. 10, and first oil groove 3322 may be spiral as shown in fig. 12. The utility model discloses bent axle 330, first oil groove 3322 and a plurality of first oil outlet 3321, every first oil outlet 3321 all communicates same first oil groove 3322 promptly. Every first oil outlet 3321 all communicates with first oil groove 3322 for every first oil outlet 3321 all leads to first oil groove 3322 with lubricating oil, it is full of sufficient lubricating oil to have guaranteed that first oil groove 3322 is full of, and can avoid the first oil groove 3322 starved condition that wherein first oil outlet 3321 of part blockked up the result in, the lubrication of major axis 332 and first bearing 212 has been guaranteed better, solve the not enough problem of bearing lubrication system fuel feeding, the reliability of major axis 332 and first bearing 212 has been improved, the operating stability of scroll compressor 1000 has been promoted.

Referring to fig. 13, it can be understood that the outer peripheral wall of the long shaft 332 is provided with a first groove 3323, and the first groove 3323 is also called a step of the crankshaft 330. The first annular groove 3323 is located in the mating region of the long shaft 332 and the first bearing 212 to prevent the first annular groove 3323 from being vented when communicating with the environment inside the housing 100. Be equipped with first oil outlet 3321 in the first annular 3323, first oil groove 3322 and first annular 3323 intercommunication to make the lubricating oil that first oil outlet 3321 flows out pass through first annular 3323 and lead to first oil groove 3322 again, thereby can ensure the lubricated oil feeding between the longer bent axle 330 of size of first bearing frame 211 and the bearing, improve the reliability of being connected between bent axle 330 and the bearing.

It can be understood that, as the scroll compressor 1000 according to the embodiment of the present invention, the inner peripheral wall of the first bearing seat 211 is provided with a second ring groove (not shown in the figure), and the second ring groove is also called a step difference of the first bearing seat 211.

The second annular groove is located in the matching area of the long shaft 332 and the first bearing 212, so that pressure relief caused by communication between the second annular groove and the environment in the shell 100 is avoided. First oil outlet 3321 is located the notch department of second annular, first oil outlet 3321 and second annular intercommunication promptly, first oil groove 3322 and second annular intercommunication to make the lubricating oil that first oil outlet 3321 flows out pass through the second annular and lead again to first oil groove 3322, thereby can ensure the lubricated oil feed between bent axle 330 and the bearing of first bearing frame 211 size long-term, improve the reliability of being connected between bent axle 330 and the bearing.

Referring to fig. 14, it can be understood that first oil groove 3322 extends in the axial direction of long shaft 332, i.e., first oil groove 3322 is linear. Second oil groove 3331 extends in the axial direction of eccentric shaft 333, i.e., second oil groove 3331 is also linear. A coordinate system is defined on a projection plane perpendicular to the axial direction of the long shaft 332, a y-axis is defined as a straight line where a connecting line of the center of the projection of the long shaft 332 and the center of the projection of the eccentric shaft 333 is located, an x-axis is defined as a straight line which passes through the center of the projection of the long shaft 332 and is perpendicular to the y-axis, a zero-angle is defined as a direction in which the y-axis faces the center of the projection of the eccentric shaft 333, and a clockwise direction is defined as an angle increasing direction.

It is understood that the projection of first oil groove 3322 is located in the range of 0 + -15 deg., i.e., -15 deg. to 15 deg.. When the first oil groove 3322 satisfies the above parameter range, that is, is located in the region B in fig. 14, the first oil groove 3322 can be disposed to avoid the load region when the long shaft 332 and the first bearing seat 211 rotate, so as to promote formation of a lubricating oil film, increase the oil film thickness in the heavy load region, improve lubrication of the long shaft 332 and the first bearing 212, further improve lubrication of the crankshaft 330 and the first bearing seat 211, and make the operation of the crankshaft 330 more stable and reliable.

The projection of the second oil groove 3331 is located in the range of 180 ± 15 °, i.e., 165 ° to 195 °. When second oil groove 3331 satisfies the above parameter range, that is, is located in region C in fig. 14, second oil groove 3331 can be disposed to avoid the load region when eccentric shaft 333 and second bearing housing 222 rotate, thereby promoting formation of a lubricating oil film, increasing the oil film thickness in the heavy load region, improving lubrication of eccentric shaft 333 and second bearing 223, further improving lubrication of crankshaft 330 and second bearing housing 222, and making operation of crankshaft 330 more stable and reliable.

Referring to fig. 15, it can be understood that second oil groove 3331 has a spiral shape, and defines the same coordinate system as the above embodiment on a projection plane perpendicular to the axial direction of long axis 332. When the rotation direction of crankshaft 330 is clockwise, the projection of second oil groove 3331 is not located in the range of 0 ° to 145 °, that is, located in the range of 145 ° to 360 °. When second oil groove 3331 satisfies the above-described parameter ranges, i.e., is located in region D in fig. 15, second oil groove 3331 can guide the lubricating oil to the opposite side of the region where eccentric shaft 333 is most loaded, thereby increasing the oil film thickness in the heavy-loaded region, improving the lubrication of eccentric shaft 333 and second bearing 223, and improving the reliability of eccentric shaft 333 and second bearing housing 222.

Referring to fig. 16, it can be understood that second oil groove 3331 has a spiral shape, and defines the same coordinate system as the above embodiment on a projection plane perpendicular to the axial direction of long axis 332. When the rotation direction of crankshaft 330 is counterclockwise, the projection of second oil groove 3331 is not located in the range of 180 ° to 325 °, that is, in the range of 325 ° to 360 °, and 0 ° to 180 °. When second oil groove 3331 satisfies the above-described parameter ranges, i.e., is located in region E in fig. 16, second oil groove 3331 is enabled to guide the lubricating oil to the opposite side of the region where eccentric shaft 333 is most loaded, thereby increasing the oil film thickness in the heavy-loaded region, improving the lubrication of eccentric shaft 333 and second bearing 223, and improving the reliability of eccentric shaft 333 and second bearing housing 222.

Referring to fig. 3, it can be appreciated that the major axis 332 has an axial diameter d1 and satisfies: d1 is less than or equal to 18 mm. For example, the axial diameter d1 of the long shaft 332 may be 18mm, 17mm, 13mm, etc., and is not limited thereto. When the shaft diameter of the crankshaft 330 is small and meets the parameter range, the scroll compressor 1000 may supply oil to the compression assembly 200 in a pressure difference oil supply manner, and has low cost and strong adaptability. The scroll compressor 1000 of the embodiment of the present invention, through setting up the crankshaft 330 having the central oil hole 331, the crankshaft 330 includes the long shaft 332 and the eccentric shaft 333, which are rotatably fitted with the movable disk 220, the outer peripheral wall of the long shaft 332 is provided with the first oil outlet hole 3321 and the first oil groove 3322 extending along the direction of the eccentric shaft 333, the outer peripheral wall of the eccentric shaft 333 is provided with the second oil groove 3331 extending along the direction of the long shaft 332, the scroll compressor 1000 employs the pressure difference oil supply mode to guide the lubricating oil inside the casing 100 to flow into the groove 213 through the central oil hole 331, and when lubricating the compression assembly 200, the first bearing 212 of the main frame 210 is lubricated by guiding the lubricating oil through the first oil outlet hole 3321 and the first oil groove 3322, the second bearing 223 of the movable disk 220 is lubricated by guiding the lubricating oil through the second oil groove 3331, thereby guiding the lubricating oil to the load area of the crankshaft 330, and avoiding the insufficient oil supply problem of the bearing lubricating system, the reliability of the crankshaft 330 and the bearings is improved, and the operation stability of the scroll compressor 1000 is improved.

Referring to FIG. 1, it can be appreciated that the scroll compressor 1000 has a displacement volume V and satisfies: v is less than or equal to 18cm³. For example, the displacement V of the scroll compressor 1000 may be 18cm³，15cm³，10cm³And the like, and are not particularly limited herein. When the discharge capacity of the scroll compressor 1000 is small and satisfies the above parameter range, the scroll compressor 1000 may supply oil to the compression assembly 200 in a differential pressure oil supply manner, which is low in cost and strong in adaptability. The utility model discloses scroll compressor 1000, through the bent axle 330 that sets up the central oilhole 331, bent axle 330 include with main frame 210 normal running fit's major axis 332 and with driving disk 220 normal running fit's eccentric shaft 333.

The outer peripheral wall of the long shaft 332 is provided with a first oil outlet hole 3321 and a first oil groove 3322 extending in the direction of the eccentric shaft 333. The outer peripheral wall of eccentric shaft 333 is provided with second oil groove 3331 extending in the direction of long axis 332. Scroll compressor 1000 adopts the mode of pressure differential fuel feeding to pass through central oilhole 331 drainage recess 213 with the inside lubricating oil of casing 100, and when lubricating compression assembly 200, guide lubricating oil through first oil outlet 3321 and first oil groove 3322 and lubricate the first bearing 212 of main frame 210, guide lubricating oil through second oil groove 3331 and lubricate the second bearing 223 of driving disk 220, thereby drainage lubricating oil to crankshaft 330's load region, avoid the problem of bearing lubrication system fuel feeding not enough, the reliability of crankshaft 330 and bearing has been improved, the operating stability of scroll compressor 1000 has been promoted.

Referring to fig. 1, an air conditioner according to an embodiment of the present invention includes a scroll compressor 1000 according to the above embodiment. The air conditioner of the present embodiment employs the scroll compressor 1000 of the first aspect embodiment, the scroll compressor 1000 is provided with a crankshaft 330 having a central oil hole 331, and the crankshaft 330 includes a long shaft 332 rotatably engaged with the main frame 210 and an eccentric shaft 333 rotatably engaged with the movable disk 220.

The outer peripheral wall of the long shaft 332 is provided with a first oil outlet hole 3321 and a first oil groove 3322 extending in the direction of the eccentric shaft 333. The outer peripheral wall of eccentric shaft 333 is provided with second oil groove 3331 extending in the direction of long axis 332. Scroll compressor 1000 leads the inside lubricating oil of casing 100 to recess 213 through central oilhole 331, and when lubricating compression assembly 200, lubricate the first bearing 212 of main frame 210 through first oil outlet 3321 and first oil groove 3322 guide lubricating oil, lubricate the second bearing 223 of driving disk 220 through second oil groove 3331 guide lubricating oil, thereby lead lubricating oil to the load region of bent axle 330, avoid the problem of bearing lubrication system fuel feeding not enough, the reliability of bent axle 330 and bearing has been improved, the operating stability of scroll compressor 1000 has been promoted, and then the operating stability of air conditioner has been promoted.

The embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made without departing from the spirit of the present invention within the knowledge of those skilled in the art.

Claims

1. A scroll compressor, comprising:

a housing having a lubricant therein;

the compression assembly is arranged in the shell and comprises a main frame, a movable disc and a static disc; the main frame is provided with a first supporting part and a groove; the movable disc is arranged on the main rack, one end of the movable disc is provided with a second supporting part, the second supporting part is positioned in the groove, and the static disc is meshed with the other end of the movable disc to form a compression cavity;

a motor disposed in the housing and having a crankshaft; a central oil hole is formed in the crankshaft, the central oil hole is used for allowing the lubricating oil to flow into the compression assembly from the interior of the shell, the crankshaft comprises a long shaft and an eccentric shaft, the long shaft penetrates through the first supporting part, an oil outlet hole and a first oil groove are formed in the peripheral wall of the long shaft, the oil outlet hole is communicated with the central oil hole, the first oil groove is communicated with the oil outlet hole and extends towards the direction of the eccentric shaft, the first oil groove is communicated with the groove, and the oil outlet hole and the first oil groove are formed in a matching area of the long shaft and the first supporting part; the eccentric shaft penetrates through the second supporting part, a second oil groove is formed in the peripheral wall of the eccentric shaft, is formed in one end face, away from the long shaft, of the eccentric shaft and extends towards the direction of the long shaft, and the second oil groove is communicated with the groove.

2. The scroll compressor of claim 1, wherein: the inside first pressure chamber that forms of casing, the internal perisporium of main frame with form the second pressure chamber between the periphery wall of driving disk, the pressure of first pressure chamber is greater than the pressure of second pressure chamber, scroll compressor passes through first pressure chamber with the fuel feeding is realized to the pressure differential of second pressure chamber.

3. The scroll compressor of claim 1, wherein: in the axial direction of the long shaft, the minimum distance between the oil outlet hole and one end, far away from the eccentric shaft, of the matching area is L, and the minimum distance satisfies the following conditions: l is more than or equal to 2 mm.

4. The scroll compressor of claim 1, wherein: the cross-sectional area of the first oil groove is S1, and satisfies: s1 is more than or equal to 1mm²(ii) a The cross-sectional area of the second oil groove is S2, and satisfies: s2 is more than or equal to 1mm²。

5. The scroll compressor of claim 1, wherein: the first oil groove extends along the axial direction of the long shaft, and the second oil groove extends along the axial direction of the eccentric shaft; on a projection plane perpendicular to the axial direction of the long shaft, a straight line on which a connecting line of the circle center of the long shaft projection and the circle center of the eccentric shaft projection of a coordinate system is located is defined as a y-axis, a straight line passing through the circle center of the long shaft projection and perpendicular to the y-axis is an x-axis, a zero angle is a direction in which the y-axis faces the circle center of the eccentric shaft projection, the clockwise direction is an angle increasing direction, the projection of the first oil groove is located within a range of 0 +/-15 degrees, and the projection of the second oil groove is located within a range of 180 +/-15 degrees.

6. The scroll compressor of claim 1, wherein: the first oil groove is spiral, and the second oil groove is spiral and has the opposite spiral direction to the first oil groove;

when the crankshaft rotates, the oil in the first oil groove flows towards the direction of the eccentric shaft, and the oil in the second oil groove flows towards the direction of the long shaft.

7. The scroll compressor of claim 6, wherein: the axial diameter of the long shaft is d1, the thread pitch of the first oil groove is m1, and the following conditions are met: m1/d1 is more than or equal to 5 and less than or equal to 10; the shaft diameter of the eccentric shaft is d2, the screw pitch of the second oil groove is m2, and the requirements are that: m2/d2 is more than or equal to 5 and less than or equal to 10.

8. The scroll compressor of claim 1, wherein: the second oil groove is spiral, on a projection plane perpendicular to the axial direction of the long shaft, a straight line which is a connection line of the circle center of the long shaft projection and the circle center of the eccentric shaft projection of a coordinate system is defined as a y-axis, a straight line which passes through the circle center of the long shaft projection and is perpendicular to the y-axis is an x-axis, a zero-angle is a direction in which the y-axis faces the circle center of the eccentric shaft projection, and a clockwise direction is an angle increasing direction;

when the rotation direction of the crankshaft is clockwise, the projection of the second oil groove is not in the range of 0-145 degrees; when the rotation direction of the crankshaft is anticlockwise, the projection of the second oil groove is not in the range of 180-325 degrees.

9. The scroll compressor of claim 1, wherein: the major axis is equipped with a plurality ofly the oil outlet, it is a plurality of that first oil groove intercommunication is a plurality of the oil outlet.

10. The scroll compressor of claim 1, wherein: the major axis is equipped with a plurality ofly oil outlet and a plurality of first oil groove, first oil groove with the oil outlet one-to-one intercommunication.

11. The scroll compressor of claim 1, wherein: the periphery wall of major axis is equipped with first annular, the oil outlet is located in the first annular, first oil groove with first annular intercommunication.

12. The scroll compressor of claim 1, wherein: the internal perisporium of first supporting part is equipped with the second annular, the oil outlet is located the notch department of second annular, first oil groove with second annular intercommunication.

13. The scroll compressor of claim 1, wherein: the axial diameter of the long shaft is d1, and satisfies: d1 is less than or equal to 18 mm; the discharge capacity of the scroll compressor is V, and the requirements are as follows: v is less than or equal to 18cm³。

14. An air conditioner, characterized in that: including a scroll compressor as claimed in any one of claims 1 to 13.