CN216306225U

CN216306225U - Rotor subassembly, compressor and air conditioner

Info

Publication number: CN216306225U
Application number: CN202122959449.9U
Authority: CN
Inventors: 龙忠铿; 武晓昆; 唐晗; 孟强军
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2021-11-26
Filing date: 2021-11-26
Publication date: 2022-04-15
Anticipated expiration: 2031-11-26

Abstract

The utility model provides a rotor assembly, a compressor and an air conditioner, comprising a first rotor with a first working part and a second working part; a second rotor having a third working portion and a fourth working portion; a second shaft body having a second channel and a third channel carrying a second rotor, and a third rotor having a fifth working portion and a sixth working portion; the second rotor and the third rotor are arranged on two sides of the first rotor, the third working part and the fifth working part are meshed with the first working part, and the fourth working part and the sixth working part are meshed with the second working part; the second rotor is provided with a first passage communicating to a meshing area between the second rotor and the first rotor, and the third passage communicates the second passage with the first passage so that the lubricant in the second passage enters the meshing area between the second rotor and the first rotor through the third passage and the first passage. The air displacement of the compressor is increased, the oil path of the rotor assembly is simplified, and the size of the compressor is reduced.

Description

Rotor subassembly, compressor and air conditioner

Technical Field

The utility model relates to the technical field of compressors, in particular to a rotor assembly, a compressor and an air conditioner.

Background

The compressor is generally arranged with a pair of parallel screw rotors placed in the spatial volume of the casing of the screw compressor. The space volume of the pair of screw rotors is periodically increased and decreased during the rotation process, so that the space volume is periodically communicated with and closed off the air inlet and the air outlet, and the processes of air suction, compression and air exhaust can be completed.

Conventionally, in order to increase the displacement of the compressor, the helical rotor structure is generally selected to be large, which results in an increase in the size of the compressor structure. And need set up the oil circuit in the compressor and lubricate the rotor, a plurality of oil circuits need be set up to a plurality of rotors in corresponding many rotors compressor to need additionally to add a plurality of structures, further lead to the structure size increase of compressor.

SUMMERY OF THE UTILITY MODEL

The embodiment of the utility model provides a rotor assembly, a compressor and an air conditioner, which can simplify the oil circuit structure of the rotor assembly to reduce the size of the compressor while increasing the displacement of the compressor.

In a first aspect, an embodiment of the present invention provides a rotor assembly, including:

a first rotor rotatable along a first axis, the first rotor including a first working portion and a second working portion;

a first shaft body carrying the first working part and the second working part;

a second rotor rotatable along a second axis, the second rotor including a third working portion and a fourth working portion;

a second shaft carrying the third working portion and the fourth working portion;

a third rotor rotatable along a third axis, the third rotor including a fifth working portion and a sixth working portion; and

a third shaft body carrying the fifth working part and the sixth working part;

the second rotor and the third rotor are respectively arranged on two opposite sides of the first rotor in the radial direction, the third working part and the fifth working part are respectively meshed with the first working part, and the fourth working part and the sixth working part are respectively meshed with the second working part;

the second rotor is provided with a first channel communicated to a meshing area between the second rotor and the first rotor, a second channel and a third channel are arranged in the second shaft body, the second channel is arranged along the axial direction of the second shaft body, and the third channel is communicated with the second channel and the first channel, so that the lubricant in the second channel enters the meshing area between the second rotor and the first rotor through the third channel and the first channel.

In an alternative embodiment of the utility model, the third working portion and the fifth working portion are symmetrically arranged with respect to the first working portion and the fourth working portion and the sixth working portion are symmetrically arranged with respect to the second working portion.

In an optional embodiment of the present invention, a fourth passage is provided on the third rotor, the fourth passage is communicated to a meshing area between the third rotor and the first rotor, a fifth passage and a sixth passage are provided in the third shaft body, the fifth passage is provided along an axial direction of the third shaft body, and the sixth passage communicates the fifth passage with the fourth passage, so that the lubricant in the fifth passage enters the meshing area between the third rotor and the first rotor through the sixth passage and the fourth passage.

In an alternative embodiment of the present invention, a first gap is provided between the second shaft body and the second rotor, and the first passage and the third passage are respectively communicated with the first gap, so that the lubricant in the second passage can sequentially flow through the third passage, the first gap and the first passage into a meshing area between the second rotor and the first rotor.

In an alternative embodiment of the present invention, a second gap is provided between the third shaft body and the third rotor, and the fourth passage and the sixth passage are respectively communicated with the second gap, so that the lubricant in the fifth passage can sequentially flow through the sixth passage, the second gap, and the fourth passage into the meshing region between the third rotor and the first rotor.

In an optional implementation manner of the present invention, the rotor assembly further includes a hydraulic device, where the hydraulic device is disposed on the first shaft, and is configured to apply an acting force to the first shaft in an axial direction of the first shaft and in a preset direction.

In an optional embodiment of the present invention, the hydraulic device includes a cylinder and a piston, the first shaft is partially inserted into the cylinder, the piston is disposed on the first shaft and located in the cylinder, the piston divides the cylinder into a first space and a second space, the second space is used for injecting liquid so that the pressure of the second space is higher than that of the first space, and the pressure difference between the second space and the first space is such that the first shaft has an acting force along the axial direction of the first shaft and towards the preset direction.

In an optional embodiment of the present invention, the rotor assembly further includes a housing, the first rotor is rotatably disposed in the housing, the cylinder is fixedly disposed outside the housing, and the first shaft extends out of the housing and is rotatably connected to the cylinder; the cylinder body is provided with a liquid inlet which is communicated with the second space.

In a second aspect, an embodiment of the present invention further provides a compressor, which includes a motor and the rotor assembly as described above, where the motor is in transmission connection with the first shaft body.

In a third aspect, an embodiment of the present invention further provides an air conditioner, including the compressor as described above.

The rotor assembly, the compressor and the air conditioner are provided with a first rotor, a second rotor and a third rotor, wherein the second rotor and the third rotor are respectively arranged on two opposite sides of the first rotor in the radial direction, the first rotor comprises a first working part and a second working part and can be meshed with the second rotor and the third rotor during the rotation of the first rotor, the third working part of the second rotor and the fifth working part of the third rotor are respectively meshed with the first working part of the first rotor, and the fourth working part of the second rotor and the sixth working part of the third rotor are respectively meshed with the second working part of the first rotor, so that four groups of rotor pairs can be formed. Therefore, the compressor provided by the embodiment of the utility model can greatly reduce the size of the compressor or realize large displacement without making the size of the compressor particularly large under the condition of the same or similar air displacement of the screw compressor in the prior art.

A first passage communicating with a meshing area between the second rotor and the first rotor is provided in the second rotor, and a second passage and a third passage communicating the second passage with the first passage are provided in the second shaft body, so that the lubricant in the second passage enters the meshing area between the second rotor and the first rotor through the third passage and the first passage and is then compressed and discharged together with the gas. The lubricant can conveniently enter the meshing area between the second rotor and the first rotor through the first channel and be discharged together with air, the lubricant does not need to be drained through other structures, the discharging structure of the lubricant is simplified, and the structural size of the compressor can be reduced.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings used in the description of the embodiments will be briefly introduced below. It is obvious that the drawings in the following description are only some embodiments of the utility model, and that for a person skilled in the art, other drawings can be derived from them without inventive effort.

For a more complete understanding of the present invention, and the advantages thereof, reference is now made to the following descriptions taken in conjunction with the accompanying drawings, wherein like reference numerals represent like parts in the following description.

Fig. 1 is a partial structural schematic view of a rotor assembly according to an embodiment of the present invention.

Fig. 2 is a partial schematic view of a compressor according to an embodiment of the present invention.

Fig. 3 is an end view of the rotor assembly of fig. 1.

Fig. 4 is a structure diagram of an oil path of the second rotor and the second shaft body according to the embodiment of the present invention.

Fig. 5 is a structural diagram of an oil path between the third rotor and the third shaft according to an embodiment of the present invention.

Fig. 6 is a first partial schematic view of the connection between the first shaft and the cylinder in fig. 2.

Fig. 7 is a second partial schematic view of the connection between the first shaft and the cylinder in fig. 2.

Fig. 8 is a third partial schematic view of the connection between the first shaft and the cylinder in fig. 2.

Fig. 9 is a fourth partial schematic view of the connection between the first shaft and the cylinder in fig. 2.

Reference numerals:

100. a compressor; 10. a motor; 20. a rotor assembly; 20a, a first bearing; 20b, a second bearing;

21. a first shaft body; 211. a first axis; 212. a first seal groove; 213. a second seal groove; 214. positioning the shaft shoulder;

22. a first rotor; 221. a first working portion; 222. a second working portion;

23. a second shaft body; 231. a second axis; 232. a second channel; 233. a third channel;

24. a second rotor; 241. a third working section; 242. a fourth working section; 243. a first channel; 244. a first gap;

25. a housing; 251. a housing body; 252. a first end cap; 2521. a first oil inlet passage; 253. a second end cap;

26. a hydraulic device; 261. a cylinder body; 2611. a first space; 2612. a second space; 2613. a liquid inlet; 2614. annular seal teeth; 262. a piston;

27. a thrust bearing;

28. a third rotor; 281. a fifth working section; 282. a sixth working section; 283. a fourth channel; 284. a second gap;

29. a third shaft body; 291. a third axis; 292. a fifth channel; 293. a sixth channel;

30. a seal ring; 40. a slip ring; 50. a fastener; 60. a flow divider; 61. a branch circuit; 62. a main road;

h1, first direction; h2, second direction.

Detailed Description

The technical solution in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It is to be understood that the described embodiments are merely exemplary of the utility model, and not restrictive of the full scope of the utility model. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, belong to the scope of protection of the present invention.

The embodiment of the utility model provides a rotor assembly, a compressor and an air conditioner, which can simplify the oil circuit structure of the rotor assembly to reduce the size of the compressor while increasing the displacement of the compressor. This will be explained below with reference to the drawings.

Referring to fig. 1 and 2, fig. 1 is a partial structural schematic view of a rotor assembly according to an embodiment of the present invention, and fig. 2 is a partial schematic view of a compressor according to an embodiment of the present invention. The compressor shown in fig. 2 may be a screw compressor, such as an opposed screw compressor. The compressor 100 may include a motor 10 and a rotor assembly 20, the motor 10 is in driving connection with the rotor assembly 20 to drive the rotor assembly 20 to rotate, wherein the rotor assembly 20 may include a first shaft 21, a first rotor 22, a second shaft 23, a second rotor 24, a third rotor 28, a third shaft 29, and a housing 25. The housing 25 may accommodate the first rotor 22, the second rotor 24, and the third rotor 28, and the housing 25 may accommodate a portion of the first shaft body 21, a portion of the second shaft body 23, and a portion of the third shaft body 29, that is, the housing 25 has an accommodation space that accommodates the first rotor 22, the second rotor 24, the third rotor 28, a portion of the first shaft body 21, a portion of the second shaft body 23, and a portion of the third shaft body 29. The first shaft body 21 carries the first rotor 22, the second shaft body 23 carries the second rotor 24, the third shaft body 29 carries the third rotor 28, and the housing 25 functions to support the first shaft body 21, the second shaft body 23, and the third shaft body 29.

It should be noted that the terms "first", "second", and the like in the description and claims of the present invention and in the drawings described above are used for distinguishing between different objects and not for describing a particular order. Furthermore, the terms "include" and "have," as well as any variations thereof, are intended to cover non-exclusive inclusions.

Referring to fig. 3 in conjunction with fig. 1, fig. 3 is a structural view of an end face of the rotor assembly shown in fig. 1. The second rotor 24 and the third rotor 28 are engaged on radially opposite sides of the first rotor 22, respectively. In an embodiment of the present invention, the first rotor 22 may be a male rotor and the second and

third rotors

24, 28 may be female rotors.

Here, the first rotor 22 as a male rotor may be understood as a driving rotor, and the second rotor 24 and the third rotor 28 as female rotors may be understood as driven rotors. For example, the first rotor 22 may be drivingly connected to a drive assembly, such as the motor 10 (including but not limited to a permanent magnet motor), and the first rotor 22 may be driven to rotate by the drive assembly, such that rotation of the first rotor 22 simultaneously rotates the second rotor 24 and the third rotor 28 together.

With continued reference to fig. 1 and fig. 2, the first rotor 22 is carried by the first shaft 21, and is in transmission connection with the motor 10 through the first shaft 21. The motor 10 may drive the first shaft 21 to rotate, and the first shaft 21 may rotate along the first axis 211 of the first shaft 21 together with the first rotor 22 carried by the first shaft. I.e., the first rotor 22 may rotate within the housing 25 along the first axis 211. In the embodiment of the present invention, the first rotor 22 may be integrally formed with the first shaft body 21. In other embodiments of the present invention, a portion of the first rotor 22 may be integrally formed with the first shaft 21, and a portion of the first rotor may be sleeved on the first shaft 21. In other embodiments of the present invention, the first rotor 22 can be directly sleeved on the first shaft 21.

Illustratively, the first rotor 22 may have at least two parts such as the first rotor 22 having a first working portion 221 and a second working portion 222, and both the first working portion 221 and the second working portion 222 may be integrally formed with the first shaft body 21. One of the first working portion 221 and the second working portion 222, such as the first working portion 221, may be integrally formed with the first shaft 21, and the other one, such as the second working portion 222, may be sleeved on the first shaft 21. Or the first working portion 221 and the second working portion 222 are both sleeved on the first shaft 21.

With continued reference to fig. 1 and 2, the first and second working

portions

221, 222 of the first rotor 22 may be helical lobes, which may also be referred to as male lobes. The number of the spiral leaves can be more than one. The first working portion 221 and the second working portion 222 of the present embodiment are configured to have opposite helical directions, i.e., the rotational directions of the first working portion 221 and the second working portion 222 are opposite. When the first rotor 22 and the second rotor 24 rotate in mesh with each other, an opposing axial force is generated between the first working portion 221 and the second working portion 222, which can also be understood as an opposing axial flow between the first working portion 221 and the second working portion 222.

It is to be noted that, in the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.

With continued reference to fig. 1 and 2, the second rotor 24 is carried by a second shaft 23, the second shaft 23 is configured to rotatably support the second rotor 24, such as the second shaft 23 is fixed to a housing 25, and the second rotor 24 is rotatable relative to the second shaft 23. The second rotor 24 is engaged with the first rotor 22 and is driven by the first rotor 22 to rotate on the second shaft 23 along the second axis 231 of the second shaft 23. The second rotor 24 may have at least two portions such as the second rotor 24 having a third working portion 241 and a fourth working portion 242, both the third working portion 241 and the fourth working portion 242 being fitted over the second shaft body 23. The third working portion 241 and the fourth working portion 242 are both rotatable within the housing 25 about the second axis 231.

The third working portion 241 engages the first working portion 221 and the fourth working portion 242 engages the second working portion 222. Wherein the third working portion 241 has a rotation direction opposite to that of the first working portion 221 and the fourth working portion 242 has a rotation direction opposite to that of the second working portion 222.

The third working portion 241 and the fourth working portion 242 of the second rotor 24 may be helical lobes, which may also be referred to as female lobes. The number of the spiral leaves can be one or more. The third working portion 241 and the fourth working portion 242 of the present embodiment are configured to have opposite helical directions, i.e., the third working portion 241 and the fourth working portion 242 have opposite rotational directions. When the first and

second rotors

22, 24 rotate in mesh with each other, an opposing axial force is generated between the third and fourth working

portions

241, 242, which may also be understood as an opposing axial flow between the third and fourth working

portions

241, 242.

With continued reference to fig. 1 and 2, the third rotor 28 is carried by a third shaft 29, the third shaft 29 is configured to rotatably support the third rotor 28, such as the third shaft 29 is fixed to the housing 25, and the third rotor 28 can rotate relative to the third shaft 29. The third rotor 28 is engaged with the first rotor 22 and can be driven by the first rotor 22 to rotate on the third shaft body 29 along the third axis 291 of the third shaft body 29. The third rotor 28 may have at least two parts such as the third rotor 28 having a fifth working portion 281 and a sixth working portion 282, the fifth working portion 281 and the sixth working portion 282 each fit over the third shaft body 29. The fifth and sixth working

portions

281, 282 are both rotatable within the housing 25 about the third axis 291.

The fifth working portion 281 engages the first working portion 221 and the sixth working portion 282 engages the second working portion 222. Wherein the fifth working portion 281 has a rotation direction opposite to that of the first working portion 221 and the sixth working portion 282 has a rotation direction opposite to that of the second working portion 222.

The fifth and sixth working

portions

281, 282 of the third rotor 28 may be helical lobes, also referred to as female lobes. The number of the spiral leaves can be one or more. The fifth working portion 281 and the sixth working portion 282 of the embodiment of the present invention are configured to have opposite spiral directions, i.e., the spiral directions of the fifth working portion 281 and the sixth working portion 282 are opposite. As the first and

third rotors

22, 28 rotate in mesh with each other, an opposing axial force is generated between the fifth and sixth working

portions

281, 282, which can also be understood as an opposing axial flow between the fifth and sixth working

portions

281, 282.

The second rotor 24 and the third rotor 28 of the embodiment of the present invention are respectively disposed at opposite sides of the first rotor 22 in a radial direction, the first rotor 22 includes a first working portion 221 and a second working portion 222 which can be engaged with the second rotor 24 and the third rotor 28 during rotation of the first rotor 22, the third working portion 241 of the second rotor 24 and the fifth working portion 281 of the third rotor 28 are respectively engaged with the first working portion 221 of the first rotor 22, and the fourth working portion 242 of the second rotor 24 and the sixth working portion 282 of the third rotor 28 are respectively engaged with the second working portion 222 of the first rotor 22, and four sets of rotor pairs can be formed, and the engagement of the first rotor 22, the second rotor 24 and the third rotor 28 of the embodiment of the present invention is equivalent to four screw compressors connected in parallel compared to the prior art. Therefore, the compressor 100 according to the embodiment of the present invention can greatly reduce the size of the compressor under the condition of the same or similar discharge capacity as that of the screw compressor in the prior art, or can realize large discharge capacity without making the size of the compressor particularly large.

In order to lubricate the first rotor 22, the second rotor 24, and the third rotor 28, please refer to fig. 4 in conjunction with fig. 1, and fig. 4 is a structural diagram of an oil path of the second rotor and the second shaft according to an embodiment of the present invention. In the embodiment of the utility model, the second rotor 24 is provided with the first channel 243, the first channel 243 is communicated to the meshing area between the second rotor 24 and the first rotor 22, the second shaft body 23 is provided with the second channel 232 and the third channel 233, the second channel 232 is arranged along the axial direction of the second shaft body 23, and the third channel 233 is used for communicating the second channel 232 with the first channel 243, so that the lubricant in the second channel 232 enters the meshing area between the second rotor 24 and the first rotor 22 through the third channel 233 and the first channel 243. The second passage 232 may introduce lubricant from the outside and contain the lubricant, and the third passage 233 may be provided in the radial direction of the second rotor 24 and communicate the second passage 232 with the meshing area between the second rotor 24 and the first rotor 22, so that the lubricant in the second passage 232 enters the meshing area between the second rotor 24 and the first rotor 22 through the third passage 233. Wherein one end of the second channel 232 may penetrate the second shaft body 23. The lubricant can be easily introduced into the meshing region between the second rotor 24 and the first rotor 22 through the first passage 243 to be discharged together with air without guiding the lubricant through other structures, thereby simplifying the lubricant discharging structure and reducing the structural size of the compressor 100.

In order to improve the lubrication effect of the first rotor 22, the second rotor 24 and the third rotor 28, please refer to fig. 5 in combination with fig. 1, and fig. 5 is a structural diagram of an oil path of the third rotor and the third shaft according to an embodiment of the present invention. An oil path may be further provided at the third rotor 28, for example, a fourth passage 283 is provided on the third rotor 28, the fourth passage 283 is communicated to a meshing region between the third rotor 28 and the first rotor 22, a fifth passage 292 and a sixth passage 293 are provided in the third shaft body 29, the fifth passage 292 is provided along the axial direction of the third shaft body 29, and the sixth passage 293 communicates the fifth passage 292 with the fourth passage 283, so that the lubricant in the fifth passage 292 enters the meshing region between the third rotor 28 and the first rotor 22 through the sixth passage 293 and the fourth passage 283. The fifth passage 292 may introduce lubricant from the outside and contain the lubricant, and the sixth passage 293 may be disposed in a radial direction of the third rotor 28 and communicate the fifth passage 292 with the mesh region between the second rotor 24 and the first rotor 22, so that the lubricant in the fifth passage 292 enters the mesh region between the third rotor 28 and the first rotor 22 through the sixth passage 293. Wherein, one end of the fifth channel 292 may penetrate the third shaft body 29.

In some embodiments, with continued reference to fig. 4, a first gap 244 is provided between the second shaft 23 and the second rotor 24, and the first channel 243 and the third channel 233 are respectively communicated with the first gap 244, so that the lubricant in the second channel 232 can flow through the third channel 233, the first gap 244 and the first channel 243 into the meshing area between the second rotor 24 and the first rotor 22. The lubricant in the second passage 232 can be facilitated to flow into the first passage 243 by providing the first gap 244, and the first gap 244 can contain the lubricant, which is more advantageous for lubrication of the first rotor 22, the second rotor 24, and the third rotor 28. The lubricant in the first gap 244 can flow into the first passage 243 due to the centrifugal force generated when the second rotor 24 rotates, and then flow to the meshing region between the second rotor 24 and the first rotor 22.

With continued reference to fig. 5, a second gap 284 is formed between the third shaft 29 and the third rotor 28, and the fourth passage 283 and the sixth passage 293 are respectively communicated with the second gap 284, so that the lubricant in the fifth passage 292 can sequentially flow through the sixth passage 293, the second gap 284 and the fourth passage 283 to enter the meshing area between the third rotor 28 and the first rotor 22. The lubricant in the second gap 284 can flow into the fourth passage 283 to communicate to the meshing region between the third rotor 28 and the first rotor 22 due to the centrifugal force generated when the third rotor 28 rotates.

In some embodiments, with continued reference to fig. 4, the rotor assembly 20 may further include a first bearing 20a, the first bearing 20a being disposed between the second rotor 24 and the second shaft 23, the second rotor 24 being rotatable about the second shaft 23 via the first bearing 20 a. The second rotor 24 is connected to the second shaft body 23 through the first bearing 20a, so that the second rotor 24 is facilitated to rotate around the second shaft body 23 through the first bearing 20 a. It will be appreciated that having the first clearance 244 between the second shaft body 23 and the second rotor 24 will be understood to have the first clearance 244 between the second rotor 24 and the first bearing 20a, and the provision of the first bearing 20a will not interfere with the communication between the third passage 233 and the first clearance 244. For example, a first communication hole may be provided in the first bearing 20a, the first communication hole communicating the third passage 233 with the first gap 244, or when a plurality of first bearings are provided, the respective first bearings 20a may be spaced apart such that a first gap is provided between the respective first bearings 20a, the first gap communicating the third passage 233 with the first gap 244, so that the lubricant may flow into the first gap 244 through the first gap.

It will be appreciated, with continued reference to fig. 5, that the rotor assembly 20 may further include a second bearing 20b, the second bearing 20b being disposed between the third rotor 28 and the third shaft 29, the third rotor 28 being rotatable about the third shaft 29 via the second bearing 20 b. The third rotor 28 is connected to the third shaft body 29 through the second bearing 20b, so that the third rotor 28 is facilitated to rotate around the third shaft body 29 through the second bearing 20 b. It is understood that having the second gap 284 between the third shaft body 29 and the third rotor 28 is understood to be having the second gap 284 between the third rotor 28 and the second bearing 20b, and the second bearing 20b is not disposed to interfere with communication between the sixth passage 293 and the second gap 284. For example, a second communication hole may be provided in the second bearing 20b, the second communication hole communicating the sixth passage 293 with the second gap 284, or when a plurality of second bearings are provided, the respective second bearings 20b may be arranged at intervals such that a second gap exists between the respective second bearings 20b, the second gap communicating the sixth passage 293 with the second gap 284, so that the lubricant may flow into the second gap 284 through the second gap.

In some embodiments, as shown in fig. 1, in order to facilitate the introduction of an external lubricant such as a lubricating oil into the second passage 232 of the second shaft body 23 and the fifth passage 292 of the third shaft body 29, a flow dividing member 60 may be provided, the flow dividing member 60 includes two branch passages 61 and a main passage 62, the two branch passages 61 and the main passage 62 are communicated with each other, one branch passage 61 and the second passage 232 of the second shaft body 23 are communicated, the other branch passage 61 and the fifth passage 292 of the third shaft body 29 are communicated, and the main passage 62 externally connects the lubricating oil, so that the external lubricating oil can be divided into the second passage 232 of the second shaft body 23 and the fifth passage 292 of the third shaft body 29 through the flow dividing member 60. The provision of the flow dividing member 60 can simplify the structure of the oil passage, thereby reducing the structural size of the compressor 100.

For the first rotor 22, the second rotor 24 and the third rotor 28, when the first rotor 22 rotates together with the second rotor 24 and the third rotor 28 by meshing with each other, due to the opposite rotation directions between the first working portion 221 and the second working portion 222, the opposite rotation directions between the third working portion 241 and the fourth working portion 242, and the opposite rotation directions between the fifth working portion 281 and the sixth working portion 282, opposite axial forces may be generated, the axial forces between the first working portion 221 and the second working portion 222 may generate a certain cancellation, the axial forces between the third working portion 241 and the fourth working portion 242 may generate a certain cancellation, and the axial forces between the fifth working portion 281 and the sixth working portion 282 may generate a certain cancellation.

It should be noted, however, that in actual production processes, it has been found that, on the one hand, there are some differences in the construction of the different parts of the first rotor 22, some differences in the construction of the different parts of the second rotor 24, and some differences in the construction of the different parts of the third rotor 28, due to manufacturing variations. And the first, second and

third rotors

22, 24, 28 may also differ from one another. The other side has some tolerance and deviation problems due to assembly, which causes some difference in fit among the first rotor 22, the second rotor 24 and the third rotor 28. This in turn results in the axial forces between the first working portion 221 and the second working portion 222 not being able to completely cancel, the axial forces between the third working portion 241 and the fourth working portion 242 not being able to completely cancel, and the axial forces between the fifth working portion 281 and the sixth working portion 282 not being able to completely cancel. The inability to rotate first rotor 22, second rotor 24, and third rotor 28 together results in nearly complete cancellation of the axial forces, yet a resultant of the axial forces in random directions is formed. As shown, the resultant axial force may be directed in the first direction H1, and the resultant axial force may be directed in the second direction H2.

On the other hand, in the product quantification of the compressor 100, the resultant axial force directions generated by the rotors in the compressors 100 are different due to the difference between the rotors in the compressors 100, for example, the resultant axial force directions of the rotors in some compressors 100 are directed toward the first direction H1, and the resultant axial force directions of the rotors in some compressors 100 are directed toward the second direction H2. That is, a resultant force with random axial direction and random numerical value occurs in the whole rotor shaft system, so that the whole shaft system is randomly pushed to one of the two exhaust end surfaces, and the exhaust end surface of the side rotor is contacted and rubbed with the end surface of the shell 25, thereby causing the occurrence of faults.

In the related art, in order to ensure that all the molded compressors 100 can stably operate, two sets of thrust bearings (or axial force bearings) are sleeved on each shaft body of the compressor 100 to limit the resultant axial force of the rotors in all the molded compressors 100, so as to ensure that all the molded compressors 100 can stably operate.

Therefore, the bearing limit of the thrust bearing is still inevitably needed, and due to the randomness of the resultant force direction, the thrust bearing needs to meet the requirement that the bearing limit can be carried in both directions, that is, in order to ensure the limitation of the resultant axial force of the rotor in the actual production and processing process of the compressor 100, the thrust bearings (axial force bearings) in both directions still need to be limited on one rotating shaft, such as the compressor 100 is provided with two sets of thrust bearings with opposite bearing directions, so as to ensure that the resultant axial force in both directions which occurs randomly is carried. For an independent compressor individual, the direction of the resultant force of the axial force which randomly occurs is always unchanged, one group of thrust bearings is used for limiting, and the other group of thrust bearings is completely idle, so that the cost performance is low, redundant mechanical loss and lubricating oil demand are added, and the failure rate of the compressor is increased. Finally, the size and the cost of the compressor assembly are increased, the mechanical efficiency of shafting operation is reduced to a certain extent, and the requirement of lubricating oil quantity is increased.

Based on this, the embodiment of the present invention provides a force along the axial direction of the first shaft 21 and toward the predetermined direction during the rotation of the first rotor 22, so that the specific direction of the axial force of the first rotor 22 in the single direction during the operation can be determined, and the relevant measures can be taken to limit the axial force of the single direction. Compared with the prior art, can all restrict the both ends of first axis body 21, and can only restrict the one end of first axis body 21 to the effect direction of this axial force can, the effectual structure size who reduces rotor assembly 20. Therefore, when the rotor assembly 20 of the embodiment of the present invention is applied to the compressor 100, the structural size of the rotor assembly 20 can be reduced without substantially affecting the displacement of the compressor 100 and without substantially affecting the stability of the compressor 100, thereby reducing the size of the compressor 100. For example, compared to the prior art in which two thrust bearings are used to limit a rotor structure, the embodiment of the present invention can use one thrust bearing 27 to limit a rotor to stably operate, so that the structural size of the rotor assembly 20 can be effectively reduced.

It should be noted that, in the related art, the compressor 100 generally arranges a pair of parallel helical rotors, such as a female rotor and a male rotor, when the pair of helical rotors works, a radial force is generated on the female rotor, and a radial force is also generated on the male rotor, so that a radial bearing needs to be arranged on the female rotor, and a radial bearing needs to be arranged on the male rotor, and the radial bearing needs to occupy a large space, so that the structural size of the compressor 100 cannot be made too small.

Based on this, as shown in fig. 1 and 3, the rotor assembly 20 provided by the embodiment of the present invention arranges the first rotor 22, the second rotor 24, and the third rotor 28 such that: the third working portion 241 of the second rotor 24 and the fifth working portion 281 of the third rotor 28 are symmetrically disposed with respect to the first working portion 221 of the first rotor 22, and the fourth working portion 242 of the second rotor 24 and the sixth working portion 282 of the third rotor 28 are symmetrically disposed with respect to the second working portion 222 of the first rotor 22. Through the structure that the symmetry set up, can roughly offset the radial force that acts on first rotor 22 to can not install the journal bearing on first rotor 22, in addition in the rotatory in-process of first rotor 22 in the above-mentioned structure, give an effort along the axial of first axis body 21 and towards predetermined direction, can only restrict one end of first axis body 21 to the effect direction of this axial force, can adopt a thrust bearing 27 to restrict a rotor and just can stable operation, make the structure size of rotor subassembly 20 effectively reduce, further reduced the structure size of compressor 100.

Wherein, in order to better counteract the radial force acting on the first rotor 22, the length, the number of the spiral blades and the end profile of the third working part 241 and the fifth working part 281 are the same; the length, number of helical lobes and end profile of the fourth working portion 242 and the sixth working portion 282 are the same.

In some embodiments, as shown in fig. 2, a hydraulic device 26 may be disposed on the first shaft body 21, and a force applied to the first shaft body 21 by the hydraulic device 26 along the axial direction of the first shaft body 21 and toward a predetermined direction ensures that the first rotor 22 and the second rotor 24 have a definite resultant axial force in a single axial direction when the first rotor 22 and the second rotor 24 are meshed with each other and rotate together. Therefore, the thrust bearing 27 is only needed to be arranged at one end of the first shaft body 21 in the embodiment of the present invention to achieve the limitation of the resultant force of the axial force in the determined single axial direction, and it can be understood that the thrust bearing 27 can limit the first shaft body 21 from moving in the direction of the thrust force, so as to ensure that the first rotor 22, the second rotor 24 and the third rotor 28 of the compressor 100 in the embodiment of the present invention can stably rotate without causing the exhaust end face of the rotor to contact and rub with the end face of the housing 25. Compared with the related art in which two thrust bearings 27 are required to be fixed to both ends of one shaft body, the compressor 100 according to the embodiment of the present invention can save a plurality of thrust bearings 27, and can reduce the overall size and cost of the compressor 100. Meanwhile, the number of the thrust bearings 27 is reduced, so that the shafting operation efficiency can be improved to a certain extent, and the requirement on the amount of lubricating oil is reduced.

It is understood that the first shaft body 21 has a first end portion and a second end portion which are oppositely arranged, the first working portion 221 and the second working portion 222 are located between the first end portion and the second end portion, and the hydraulic device 26 may be arranged on the first end portion or the second end portion of the first shaft body 21, as long as it can apply a force to the first shaft body 21 along the axial direction of the first shaft body 21 and towards a preset direction. For example, as shown in the drawings, the preset direction may be a direction along the axial direction of the first shaft body 21 and toward the motor 10, and at this time, a direction along the axial direction of the first shaft body 21 and toward the motor 10 may be defined as a first direction H1, and a direction opposite to the first direction H1 may be defined as a second direction H2. For example, referring to fig. 2, the hydraulic device 26 is disposed at an end of the first shaft 21 close to the motor 10, and the hydraulic device 26 applies a predetermined acting force in the first direction H1 to the first shaft 21, it can be understood that the predetermined acting force in the first direction H1 applied by the hydraulic device 26 needs to be: the first shaft body 21 can be made to have the resultant axial force along the first direction H1, and the first rotor 22, the second rotor 24 and the third rotor 28 have the determined resultant axial force facing the first direction H1, and then the resultant axial force in the determined direction can be limited by taking relevant measures according to the resultant axial force in the determined direction, such as providing a thrust bearing 27 at one end of the first shaft body 21, and limiting the resultant axial force in the determined direction by the thrust bearing 27. Since the space of the end of the first shaft 21 close to the motor 10 is small, the thrust bearing 27 may be installed at the end of the first shaft 21 away from the motor 10 in order to facilitate the installation of the thrust bearing 27. Of course, if the space allows, the thrust bearing 27 may be disposed at one end of the first shaft body 21 close to the motor 10, and it is understood that the specific location of the thrust bearing 27 may be selected according to the specific situation, as long as it can play a role of limiting the movement of the first shaft body 21 in the direction of the force.

In order to more clearly explain the structure of the hydraulic device 26, the specific structure of the hydraulic device 26 will be described below with reference to the drawings.

For example, the hydraulic device 26 of the embodiment of the present invention may apply the force by using high-pressure oil, and of course, other liquids that do not have a great influence on the compressor 100 may be used, and the present invention is not limited thereto.

As shown in fig. 1, the hydraulic device 26 may include a cylinder 261 and a piston 262, the cylinder 261 is fixedly disposed outside the housing 25, one end of the first shaft 21 penetrates through the housing 25 and the cylinder 261, the piston 262 is disposed on the first shaft 21 and located in the cylinder 261, wherein the piston 262 divides the cylinder 261 into a first space 2611 and a second space 2612, the second space 2612 is used for injecting liquid to make the pressure of the second space 2612 greater than that of the first space 2611, when the pressure difference is formed between the second space 2612 and the first space 2611, the liquid exerts a force towards the first space 2611 on the piston 262, since the piston 262 is provided on the first shaft body 21, the force can also act on the first shaft body 21, that is, a pressure difference is formed between the second space 2612 and the first space 2611, so that the first shaft body 21 has a force along the axial direction of the first shaft body 21 and toward a predetermined direction. For example, as shown in the figure, the first space 2611 is located on one side of the piston 262 close to the motor 10, the second space 2612 is located on one side of the piston 262 away from the motor 10, a fluid inlet 2613 is arranged on the cylinder 261, the fluid inlet 2613 is communicated with the second space 2612, at this time, the fluid inlet 2613 may be externally connected with an oil pump, and the oil pump injects high-pressure oil into the second space 2612 through the fluid inlet 2613, so that the pressure of the high-pressure oil acting on the piston 262 can be transmitted to the first shaft body 21 through the piston 262, and the first shaft body 21 has an acting force (i.e., an acting force facing to the first direction H1) along the axial direction of the first shaft body 21 and in the direction of the first space 2611.

Certainly, in other embodiments, also can be that first space is located the one side that the piston deviates from the motor, and the second space is located the one side that the piston is close to the motor, is provided with the inlet on the cylinder body, inlet and second space intercommunication, and the inlet can external oil pump this moment, and high-pressure oil is injected into to the second space through this inlet to the oil pump to the pressure that high-pressure oil was used in on the piston can be transmitted for first axis body through the piston, and then makes first axis body have the axial of following first axis body and towards the effort of second direction H2.

In order to fully utilize the spatial structure of the rotor assembly 20, a liquid inlet channel of high-pressure oil may be combined with the shaft body, such as the liquid inlet channel of high-pressure oil may be combined with one of the second shaft body 23 or the third shaft body 29, such as, as shown in fig. 1, the second channel 232 of the second shaft body 23 is introduced into the high-pressure oil, the second channel 232 penetrates through the second shaft body 23 along the axial direction of the second shaft body 23, that is, the second shaft body 23 may be made into a hollow structure, one end of the second channel 232 is communicated with the liquid inlet 2613 of the hydraulic device 26, and one end of the second channel 232, which is far away from the liquid inlet 2613, may be used for liquid inlet, that is, the high-pressure oil may flow to the liquid inlet 2613 through the first channel 243 of the second shaft body 23. It can be understood that the high-pressure oil can be high-pressure oil with a lubricating effect, so that the high-pressure oil can play a role in both high pressure and lubrication.

For example, with continued reference to fig. 2, the housing 25 may include a housing body 251, a first end cap 252 and a second end cap 253, the housing body 251 is used for accommodating the first rotor 22, the second rotor 24 and the third rotor 28, the first end cap 252 is disposed on one side of the housing body 251, the second end cap 253 is disposed on the other side of the housing body 251 opposite to the one side, such as the first end cap 252 is disposed on one side of the housing body 251 close to the motor 10, the second end cap 253 is disposed on one side of the housing body 251 away from the motor 10, one end of the first shaft body 21 is rotatably connected to the first end cap 252, the other end of the first shaft body 21 is rotatably connected to the second end cap 253, and the thrust bearing 27 may be disposed on the first end cap 252 or the second end cap 253.

As shown in fig. 2, in order to facilitate the flow of liquid, a first oil inlet passage 2521 is disposed on the first end cover 252, the cylinder body 261 is disposed on the first end cover 252, a liquid inlet 2613 on the cylinder body 261 is communicated with one end of the first oil inlet passage 2521, and the other end of the first oil inlet passage 2521 is communicated with the second passage 232 of the second shaft body 23, so that external high-pressure oil can be flowed from the first oil inlet passage 2521 into the second space 2612.

Since the piston 262 is pressurized by the liquid, in order to prevent the liquid from leaking out of the cylinder 261, a sealing structure may be provided at the connection between the first shaft 21 and the cylinder 261, it can be understood that the first shaft 21 is rotatably connected with the cylinder 261, please refer to fig. 6, and fig. 6 is a first partial schematic view of the connection between the first shaft and the cylinder in fig. 2. Labyrinth seal can be adopted at the joint of the first shaft body 21 and the cylinder body 261, namely a plurality of annular seal teeth 2614 which are arranged in sequence can be arranged on the cylinder body 261, a series of closure gaps and expansion cavities are formed between the teeth, and the liquid generates throttling effect when passing through the gaps of the zigzag labyrinth to achieve the purpose of leakage resistance. Of course, a plurality of annular sealing teeth 2614 arranged in sequence may be provided on the first shaft body 21. In another embodiment, please refer to fig. 7, fig. 7 is a second partial schematic view of a connection between the first shaft and the cylinder in fig. 2. A gap seal may be employed at the connection of the first shaft body 21 and the cylinder body 261, that is, a sealing function with a slight gap between the moving members. Because the clearance exists between the matching parts, the friction force is small, the heat generation is less, the service life is long, and the structure is simple and compact and the size is small because no sealing material is used. In other embodiments, please refer to fig. 8, fig. 8 is a third partial schematic view of a connection between the first shaft and the cylinder in fig. 2. The connection between the first shaft 21 and the cylinder 261 may be sealed by using a sealing ring 30, that is, a first sealing groove 212 for mounting the sealing ring 30 may be disposed on the first shaft 21, the sealing ring 30 is sleeved in the first sealing groove 212, and the sealing between the first shaft 21 and the cylinder 261 is realized by using the sealing ring 30, wherein the sealing ring 30 may be an O-ring. In another embodiment, please refer to fig. 9, fig. 9 is a fourth partial schematic view of a connection between the first shaft and the cylinder in fig. 2. The connecting portion between the first shaft body 21 and the cylinder body 261 can be sealed by the sliding ring 40, that is, the first shaft body 21 is provided with the second sealing groove 213 for installing the sliding ring 40, the sliding ring 40 is sleeved in the second sealing groove 213, and the sliding ring 40 is used to seal the first shaft body 21 and the cylinder body 261.

It can be understood that, since the cylinder 261 is finally sealed in the casing 25 of the compressor 100, there may be a slight leakage at the joint of the first shaft 21 and the cylinder 261, that is, a small amount of leaked liquid enters the circulation of the compressor 100 without causing a great influence on the compressor 100, and at this time, there is no great requirement for the sealing performance at the joint of the first shaft 21 and the cylinder 261.

The first shaft 21 is driven to rotate by the motor 10, and at this time, the piston 262 may be configured to rotate together with the first shaft 21, that is, the piston 262 is fixedly disposed on the first shaft 21, the piston 262 is movable relative to the cylinder 261, and in order to prevent the liquid in the second space 2612 from flowing to the first space 2611, the piston 262 is disposed in a sealed manner with the inner side wall of the cylinder 261. For example, a labyrinth seal may be used between the piston 262 and the cylinder 261, or a clearance seal may be used between the piston 262 and the cylinder 261. It is understood that there is no need for an excessive requirement for sealing between the piston 262 and the inner side wall of the cylinder 261, that is, the liquid in the second space 2612 may leak into the first space 2611 in a small amount, and as long as the leakage amount of the liquid is significantly smaller than the supply amount of the liquid, the liquid may exert sufficient pressure on the piston 262, that is, the hydraulic device 26 may act to exert a force on the piston 262 in the axial direction of the first shaft body 21 and toward a predetermined direction.

The piston 262 is fixedly disposed on the first shaft 21, and the piston 262 and the first shaft 21 are in interference fit. As shown in fig. 2, a positioning shoulder 214 may be provided on the first shaft body 21, the piston 262 may abut against the positioning shoulder 214, a fastener 50 may be provided on a side of the piston 262 facing away from the positioning shoulder 214, and the fastener 50 may fix the piston 262 to the first shaft body 21 together with the positioning shoulder 214. Wherein the fastener 50 may be a nut that is tightened onto the first shaft body 21 and that cooperates with the retaining shoulder 214 to secure the piston 262 on the first shaft body 21.

Embodiments of the present invention also provide an air conditioner including the compressor 100 as defined in combination with one or more of the above embodiments.

In the foregoing embodiments, the descriptions of the respective embodiments have respective emphasis, and for parts that are not described in detail in a certain embodiment, reference may be made to related descriptions of other embodiments.

The rotor assembly, the compressor and the air conditioner provided by the embodiment of the utility model are described in detail, the principle and the embodiment of the utility model are explained by applying specific examples, and the description of the embodiment is only used for helping to understand the method and the core idea of the utility model; meanwhile, for those skilled in the art, according to the idea of the present invention, there may be variations in the specific embodiments and the application scope, and in summary, the content of the present specification should not be construed as a limitation to the present invention.

Claims

1. A rotor assembly, comprising:

a first shaft body carrying the first working part and the second working part;

a third shaft body carrying the fifth working part and the sixth working part;

2. The rotor assembly of claim 1 wherein the third and fifth working portions are symmetrically disposed with respect to the first working portion and the fourth and sixth working portions are symmetrically disposed with respect to the second working portion.

3. The rotor assembly of claim 1 wherein a fourth passage is provided on the third rotor, the fourth passage communicating to a meshing area between the third rotor and the first rotor, a fifth passage and a sixth passage being provided in the third shaft, the fifth passage being disposed axially of the third shaft, the sixth passage communicating the fifth passage with the fourth passage such that lubricant within the fifth passage enters the meshing area between the third rotor and the first rotor through the sixth passage and the fourth passage.

4. The rotor assembly of claim 3 wherein a first gap is provided between the second shaft and the second rotor, the first and third passages each communicating with the first gap such that lubricant in the second passage can flow through the third passage, the first gap and the first passage in sequence into a meshing area between the second rotor and the first rotor.

5. The rotor assembly of claim 3 or 4 wherein a second gap is provided between the third shaft body and the third rotor, and the fourth and sixth passages are in communication with the second gap, respectively, such that lubricant in the fifth passage can flow through the sixth passage, the second gap, and the fourth passage in sequence into the meshing area between the third rotor and the first rotor.

6. The rotor assembly of any one of claims 1-4 further comprising a hydraulic device disposed on the first shaft for applying a force to the first shaft in an axial direction of the first shaft and in a predetermined direction.

7. The rotor assembly of claim 6, wherein the hydraulic device comprises a cylinder and a piston, the first shaft is partially inserted into the cylinder, the piston is arranged on the first shaft and located in the cylinder, the piston divides the cylinder into a first space and a second space, the second space is used for injecting liquid so that the pressure of the second space is higher than that of the first space, and the pressure difference between the second space and the first space enables the first shaft to have acting force along the axial direction of the first shaft and towards the preset direction.

8. The rotor assembly of claim 7 further comprising a housing, wherein the first rotor is rotatably disposed within the housing, wherein the cylinder is fixedly disposed outside the housing, and wherein the first shaft extends out of the housing and is rotatably coupled to the cylinder; the cylinder body is provided with a liquid inlet which is communicated with the second space.

9. A compressor comprising a motor and a rotor assembly as claimed in any one of claims 1 to 8, the motor being in driving connection with the first shaft.

10. An air conditioner characterized by comprising the compressor of claim 9.