CN215256812U - Compressor and air conditioner - Google Patents

Abstract

The application discloses compressor and air conditioner, a compressor includes: the first rotor assembly comprises a first rotor, a second rotor and a first shaft body, the first rotor and the second rotor are coaxially arranged, the thread turning directions are opposite, the first shaft body bears and drives the first rotor and the second rotor to rotate, the first shaft body comprises a first end positioned in the axial direction of the first shaft body, and the first end is provided with a flat position for transmission; and the second rotor assembly comprises a third rotor and a fourth rotor which are coaxially arranged, the third rotor is meshed with the first rotor, and the fourth rotor is meshed with the second rotor. Compare in setting up the keyway on first end to make first axis body and motor realize the drive mode that the keyway is connected, the slotted hole need not to be seted up to the first axis body of this application, makes the intensity and the bending resistance of first axis body higher, is applicable to more in the less small-size screw compressor of first axis body diameter.

Description

Compressor and air conditioner

Technical Field

The application belongs to the technical field of refrigeration equipment, and particularly relates to a compressor and an air conditioner.

Background

The compressor is generally arranged with a pair of parallel screw rotors disposed within the spatial volume of the housing of the screw compressor. The space volume of the shell of the compressor is periodically increased and decreased during the rotation of the pair of screw rotors, 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. The rotating shaft of one spiral rotor in the pair of spiral rotors is in key groove connection with the motor, so that the motor can drive the pair of spiral rotors to rotate. However, in a small screw compressor, the rotating shaft of the screw rotor is small, and the strength of the rotating shaft is reduced by forming a key groove in the rotating shaft.

Disclosure of Invention

The embodiment of the application provides a compressor and an air conditioner, and aims to solve the problem that the strength of the joint of a first rotor assembly and a motor is insufficient.

The embodiment of the application provides a compressor, includes:

the first rotor assembly comprises a first rotor, a second rotor and a first shaft body, the first rotor and the second rotor are coaxially arranged, the thread turning directions are opposite, the first shaft body bears and drives the first rotor and the second rotor to rotate, the first shaft body comprises a first end located in the axial direction of the first shaft body, and the first end is provided with a flat position for transmission; and

the second rotor assembly comprises a third rotor and a fourth rotor which are coaxially arranged, the third rotor is meshed with the first rotor, and the fourth rotor is meshed with the second rotor.

In an optional embodiment of the present application, the flat position is provided in a plurality of numbers, and the plurality of flat positions are uniformly provided along a circumferential direction of the first shaft body.

In an optional embodiment of the present application, an arc surface is formed between two adjacent flat positions.

In an optional embodiment of the present application, the flat portion has a first transmission plane and a thrust surface, the first transmission plane is parallel to the axial direction of the first shaft, the thrust surface is perpendicularly connected to the first transmission plane, and the thrust surface is located on a side of the first transmission plane close to the first rotor.

In an optional embodiment of the present application, a ratio of a distance from the first transmission plane to the first end axis to the first end radius is a, where a is greater than or equal to 0.75 and less than or equal to 0.85.

In an optional implementation of this application, still include the motor, the motor has electric motor rotor, electric motor rotor has the mounting hole, first end part set up in the mounting hole forms the lateral wall of mounting hole be equipped with the second transmission plane of first transmission plane laminating.

In an alternative embodiment of the present application, the first end has a first end surface located at an axial end of the first shaft, the first end surface is perpendicularly connected to the first transmission plane, the first end surface is provided with a lock member, and the motor rotor is interposed between the lock member and the thrust surface.

In an alternative embodiment of the present application, the first shaft body has a first bearing installation section connected to the first end, and the first bearing installation section has a machining accuracy different from that of the first end.

In an alternative embodiment of the present application, the first end is not equal in diameter to the first bearing mounting section.

The embodiment of the application also provides an air conditioner, which comprises the compressor.

In this application embodiment, the first end of first axis body is through the transmission of the motor rotor of flat position and motor for the first rotor of motor drive and second rotor rotate, and first rotor and second rotor pivoted in-process drive third rotor and fourth rotor rotate, and then accomplish breathing in, compression and carminative process of compressor. It can be understood that, compared with a transmission mode that the first end is provided with the key groove to enable the first shaft body and the motor to be connected through the key groove, the first shaft body of the embodiment of the application does not need to be provided with a slotted hole, so that the strength and the bending resistance of the first shaft body are higher.

Drawings

The technical solutions and advantages of the present application will become apparent from the following detailed description of specific embodiments of the present application when taken in conjunction with the accompanying drawings.

Fig. 1 is a partial schematic view of a first compressor according to an embodiment of the present disclosure.

Fig. 2 is a partial structural view of the compressor shown in fig. 1 after one of the housings is assembled.

Fig. 3 is a first structural schematic diagram of the first shaft of the compressor shown in fig. 1.

Fig. 4 is a second structural diagram of the first shaft of the compressor shown in fig. 1.

Fig. 5 is a cross-sectional view of the first shaft body shown in fig. 4 in a P-P direction.

Fig. 6 is a partial structural schematic view of the first shaft and the motor rotor shown in fig. 4.

The reference numbers in the figures are respectively:

100. a compressor;

10. a housing; 11. a first exhaust port; 12. a second exhaust port; 13. an air suction port;

20. a first rotor assembly; 21. a first rotor; 22. a second rotor; 23. a first shaft body; 231. a first end; 232. a first bearing mounting section; 231. a first end; 2311. flattening; 2312. a cambered surface; 2313. a first plane of transmission; 2314. a thrust surface; 2315. a first end face; 232. a first bearing mounting section; 233. a first rotor assembly mounting section; 234. a second bearing mounting section;

30. a second rotor assembly; 31. a third rotor; 32. a fourth rotor; 33. a second shaft body;

40. a motor; 41. a motor rotor; 411. mounting holes; 412. a second transmission plane;

50. a locking member;

61. a first bearing; 62. a second bearing; 63. a third bearing; 64. a fourth bearing;

l1, distance from the first transfer plane to the axis of the first end;

l2, radius of first end;

l3, tangent line of the connection of cambered surface and the first transmission plane.

Detailed Description

The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. It is to be understood that the embodiments described are only a few embodiments of the present application and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.

The embodiment of the application provides a compressor and an air conditioner.

Referring to fig. 1, fig. 1 is a partial schematic view of a first compressor according to an embodiment of the present disclosure. Embodiments of the present application provide a compressor 100 that may be a screw compressor, such as where the compressor 100 is an opposed screw compressor. The compressor 100 may be applied to an air conditioner to perform a gas compression operation of the air conditioner. The air conditioner can be a hanging type air conditioner, a cabinet type air conditioner, a ceiling type air conditioner, a window type air conditioner or a central air conditioner and the like.

Referring to fig. 2, fig. 2 is a partial structural schematic view of the compressor shown in fig. 1 after one of the shells is assembled. As shown in fig. 1 and 2, the compressor 100 may include a casing 10, a first rotor assembly 20, a second rotor assembly 30, and a motor 40. The housing 10 may house a portion of the first rotor assembly 20 and a portion of the second rotor assembly 30. The portion of the first rotor assembly 20 located within the housing 10 meshes with the portion of the second rotor assembly 30 located within the housing 10. The first rotor assembly 20 is in drive communication with a motor 40. In turn, the motor 40 can drive the first rotor assembly 20 to rotate and the first rotor assembly 20 can drive the second rotor assembly 30 to rotate. Finally, the first and second rotor assemblies 20 and 30 rotate synchronously to complete the suction, compression and discharge actions of the compressor 100.

In the embodiment of the present application, as shown in fig. 2, the housing 10 may have a receiving space that receives a portion of the first rotor assembly 20 and a portion of the second rotor assembly 30. The casing 10 also has a first exhaust port 11, a second exhaust port 12, and an intake port 13 communicating with an accommodation space for accommodating a portion of the first rotor assembly 20 and a portion of the second rotor assembly 30. The suction port 13 serves to transmit the gas outside the casing 10 to the receiving space inside the casing 10 when the first and second rotor assemblies 20 and 30 are rotated in mesh. The first exhaust port 11 and the second exhaust port 12 are used to compress the gas in the accommodating space of the casing 10 to the outside of the casing 10 when the third rotor 31 and the fourth rotor 32 are rotated in mesh. Thus, processes of suction, compression, and discharge of the compressor 100 may be realized. The first exhaust port 11 and the second exhaust port 12 are located at both ends of the casing 10 in the axial direction of the second shaft body 33.

The first rotor assembly 20 includes a first rotor 21, a second rotor 22, and a first shaft body 23. Illustratively, the first rotor 21 and the second rotor 22 are coaxially arranged and have opposite rotation directions. The first shaft 23 carries and drives the first rotor 21 and the second rotor 22 in rotation.

It can be understood that, in the technical solution before the improvement, a key groove is formed at the end of the first shaft 23, and a positioning key is arranged in the key groove, and after the transmission component of the motor 40 is sleeved at the end of the first shaft 23, the transmission component of the motor 40 is engaged with the positioning key to drive the first shaft 23 to rotate. However, for some screw compressors with smaller displacement, such as a screw compressor with displacement less than 100m3/h, or a screw compressor with displacement less than 75m3/h, or a screw compressor with displacement less than 125m3/h, the diameter of the first shaft body 23 is smaller. If the positioning key is used for driving, the strength and the bending resistance of the first shaft 23 are reduced by forming the positioning key slot, so that the first shaft 23 is difficult to meet the requirement of the shearing force in the rotating process. Further, the positioning key groove is formed in the first shaft body 23 having a small diameter, which is difficult to machine.

Referring to fig. 3 and 4, fig. 3 is a first structural schematic diagram of a first shaft of the compressor shown in fig. 1, and fig. 4 is a second structural schematic diagram of the first shaft of the compressor shown in fig. 1. As shown in fig. 3, in the present embodiment, the first shaft body 23 may include a first end 231, a first bearing mounting section 232, a first rotor assembly mounting section 233, and a second bearing mounting section 234, which are connected in sequence, in the axial direction thereof. The first bearing mounting section 232 of the first shaft body 23 can be rotatably mounted on the housing 10 through the first bearing 61, and the second bearing mounting section 234 of the first shaft body 23 can be rotatably mounted on the housing 10 through the second bearing 62.

The first end 231 may be provided with a flat 2311. Accordingly, the transmission member of the motor 40 for driving the first shaft 23 may be provided with a flat hole having a cross-section identical to the cross-section of the flat portion 2311 of the first end 231. And the transmission part of the motor 40 can push the flat part 2311 to rotate around the axis of the first shaft body 23 through the engagement of the flat part 2311 and the flat hole. It can be understood that, in the embodiment of the present application, a structure that the flat portion 2311 of the first shaft body 23 is in transmission with the motor 40 is adopted, and a positioning key groove does not need to be formed at the first end 231 of the first shaft body 23, so that on one hand, the processing cost and the processing difficulty are reduced, and on the other hand, the overall strength and the bending resistance of the first shaft body 23 are improved.

In the embodiment of the present application, the flat portion 2311 may be provided in plurality. The plurality of flat portions 2311 are evenly distributed around the circumference of the first shaft body 23. Illustratively, as shown in fig. 4, there are two flat portions 2311, and the two flat portions 2311 are not only uniformly distributed along the circumferential direction of the first shaft body 23, but also symmetrically arranged about the axis of the first shaft body 23. Still alternatively, as shown in fig. 3, there are three flat positions 2311, and an included angle of 120 ° is formed between every two of the three flat positions 2311 with respect to the axis of the first shaft body 23. Of course, in some other specific embodiments, the number of the flat portions 2311 may be four or five, and the like, which is not limited in this embodiment of the application.

It is understood that a plurality of flat portions 2311 are uniformly distributed along the circumferential direction of the first shaft body 23, so that the first shaft body 23 facilitates the balance correction. In contrast, if only one flat portion 2311 is disposed on the first end 231, or the cross section of the transmission portion of the first end 231 is an asymmetric irregular shape, an imbalance may be caused during the rotation of the first shaft body 23, i.e., centrifugal inertia forces generated at various positions during the rotation of the first shaft body 23 cannot be cancelled out. On the one hand, when the first shaft body 23 itself is subjected to centrifugal inertial force and the diameter of the first shaft body 23 is small, the accommodation causes the first shaft body 23 to bend or even break, thereby affecting the stability of the operation of the first rotor assembly 20. On the other hand, the centrifugal inertial force directly affects the stability of the first rotor 21 and the second rotor 22 after being applied to the first rotor 21 and the second rotor 22. Therefore, the compressor 100 provided by the embodiment of the present application is arranged to be uniformly arranged around the circumference of the first shaft body 23 by setting the flat portion 2311 of the first end 231, so that the first shaft body 23, the first rotor 21 and the second rotor 22 are more stable and reliable in operation and are not easily damaged, and further, the stability and the service life of the compressor 100 provided by the embodiment of the present application are improved.

In the embodiment of the present application, an arc surface 2312 may be formed between adjacent flat portions 2311. Illustratively, the peripheral sidewall of the first end 231 is formed by a plurality of cambered surfaces 2312 and a plurality of flat portions 2311 which are alternately arranged at intervals. For example, as shown in fig. 4, the peripheral sidewall of the first end 231 is formed by two flat portions 2311 and two curved surfaces 2312 alternately arranged at intervals. Alternatively, as shown in fig. 3, the peripheral sidewall of the first end 231 is formed by three flat portions 2311 and three curved surfaces 2312 alternately arranged at intervals. The specific number of the flat portions 2311 and the cambered surfaces 2312 is not limited in the embodiment of the application, and the number of the flat portions 2311 is equal to that of the cambered surfaces 2312. It can be understood that, for the structure in which the arc surface 2312 is formed between the adjacent flat portions 2311, in the manufacturing process, after the first end 231 of the first shaft body 23 is formed into a cylindrical shape, the flat portions 2311 are directly processed on the first end 231 in a milling manner, so that the first shaft body 23 provided by the embodiment of the present application has an advantage of easy processing.

As shown in fig. 4, the flat portion 2311 may include a first drive flat 2313 and a thrust surface 2314. In the embodiment of the present application, the first transmission plane 2313 is parallel to the axial direction of the second shaft body 33. An arc surface 2312 is formed between adjacent first transmission planes 2313. The thrust surface 2314 is perpendicularly connected to the first transmission plane 2313, and the thrust surface 2314 is located on the side of the first transmission plane 2313 close to the first rotor 21. Therefore, in the process of machining the flat portion 2311, the first shaft body 23 may be clamped to a chuck of a lathe, and the flat portion 2311 may be milled by a tool fed and milled in the axial direction toward the first rotor 21 from the side of the first end 231 away from the first rotor 21 in a turning and milling manner.

Referring to FIG. 5, FIG. 5 is a cross-sectional view of the first shaft shown in FIG. 4 taken along the direction P-P. In the embodiment of the present application, in the connecting arc surface 2312 and the first transmission plane 2313, an included angle between a tangent L3 at the connection point of the arc surface 2312 and the first transmission plane 2313 is greater than 90 ° toward the axis of the first shaft body 23. In the actual manufacturing process, heat treatment is required after the first shaft body 23 is processed, and if the included angle between the tangent line L3 at the joint of the arc surface 2312 and the first transmission plane 2313, which face the axial line of the first shaft body 23, is smaller than 90 °, stress release is not uniform in the heat treatment process at the joint of the arc surface 2312 and the first transmission plane 2313, and fine cracks are generated at the joint of the arc surface 2312 and the first transmission plane 2313. When the diameter of the first shaft body 23 is small, the influence of the micro cracks on the first shaft body 23, the first rotor 21 and the second rotor 22 is further amplified, and finally, the operation stability and the service life of the first shaft body 23, the first rotor 21 and the second rotor 22 are affected. Therefore, the first shaft 23, the first rotor 21 and the second rotor 22 provided by the embodiment of the present application have the advantages of high stability and long service life.

As shown in FIG. 5, the ratio of the distance L1 from the first transmission plane 2313 to the axis of the first end 231 to the radius L2 of the first end 231 is A, wherein A is greater than or equal to 0.75 and less than or equal to 0.85. When a is greater than 0.85, the circumferential side of the first end 231 of the first transmission plane 2313 is small, so that the circumferential side of the first end 231 is more similar to a cylindrical surface, and the motor 40 easily slips from the flat portion 2311 in the process that the motor 40 drives the first shaft body 23 to rotate through the flat portion 2311. When a < 0.75, the thickness of the first end 231 in the radial direction is too small, the strength and bending resistance of the first end 231 itself are deteriorated, and the first end 231 of the first shaft body 23 is easily bent or even broken. Therefore, the first shaft body 23 provided by the embodiment of the present application has the advantages of high structural strength and stable operation.

The motor 40 may be directly connected to the first end 231 to drive the first shaft 23 to rotate, or the motor 40 may also be indirectly connected to the first end 231 through a speed reducer or a coupling, etc. to drive the first shaft 23 to rotate. In the following, the technical solution of the embodiment of the present application is further explained by taking the case that the motor 40 is directly connected to the first end 231.

Referring to fig. 6, fig. 6 is a partial structural schematic view of the first shaft and the motor rotor shown in fig. 4. The motor 40 may include a motor stator and a motor rotor 41. The motor rotor 41 has a mounting hole 411 such that the motor rotor 41 is sleeved on a portion of the first end 231. The motor stator is arranged around the motor rotor 41. And the second rotating shaft can be driven to rotate when the motor rotor 41 rotates.

As shown in fig. 6, the cross-section of the mounting hole 411 is the same as the cross-section at the flat portion 2311 of the first end 231. Therefore, the side wall forming the mounting hole 411 includes the second transmission plane 412 abutting against the first transmission plane 2313, so that the first transmission plane 2313 can be pushed to rotate around the axis of the first shaft body 23 through the second transmission plane 412 during the rotation of the motor rotor 41. Eventually, the first shaft body 23 can drive the first rotor assembly 20 to rotate.

It can be understood that, compared with the above-mentioned prior art in which the motor rotor 41 is connected with the first end 231 through the positioning key, the embodiment of the present application provides that the first transmission plane 2313 and the second transmission plane 412 are abutted against each other, so that the transmission matching area of the motor rotor 41 and the first shaft body 23 is greatly increased, and further, the connection between the motor rotor 41 and the first shaft body 23 is more stable and the stress is more uniform. On the other hand, in the embodiment of the present application, because the strength of the first shaft 23 is increased, the first shaft 23 is more stable in operation and is not easy to bend, and it is further ensured that the motor rotor 41 sleeved on the first end 231 does not shake during the rotation process. Finally, the motor rotor 41 is prevented from shaking in the radial direction during rotation, so that the motor rotor 41 and the motor stator are prevented from being worn. Therefore, the compressor 100 provided by the embodiment of the present application has the advantage of long service life.

As shown in fig. 6, the first end 231 has a first end face 2315 located at an axial end of the first shaft body 23, the first end face 2315 is provided with the lock member 50, the first end face 2315 is perpendicularly connected with the first transmission plane 2313, and the motor rotor 41 is sandwiched between the lock member 50 and the thrust surface 2314.

In the above technical solution before improvement, the positioning key is used to connect with the motor rotor 41, and the first end 231 is further required to be provided with two limiting steps at two axial sides of the positioning key to install two limiting bearings, so as to axially limit the motor rotor 41 through the two limiting bearings. However, in standard components, the diameter of the bearing is typically an integer multiple of 5, and the motor 40 has only a few specifications. When the diameter of the motor rotor 41 is smaller, the diameter of the limit bearing is also relatively smaller, the diameter of the first end 231 is also smaller, and the difference between the diameters of the positioning key part and the limit step arranged in the first end 231 should meet the installation requirement of the limit bearing, which directly results in that the difference between the diameters of the positioning key part and the limit step arranged in the first end 231 is smaller. Therefore, the formed limit step has a weak fixing ability for the limit bearing, and when the motor rotor 41 rotates too fast, the limit bearing cannot effectively limit the axial play of the motor rotor 41, even if the motor rotor 41 is installed unstably, the axial play of the first shaft 23 may occur during the movement of the motor rotor 41. In contrast, in the embodiment of the present application, the thrust surface 2314 of the flat portion 2311 and the locking member 50 limit the axial movement of the motor rotor 41, so that on one hand, the installation structure of the motor rotor 41 is simplified, a plurality of limit bearings are omitted, and on the other hand, the axial limit effect of the motor rotor 41 is improved.

As shown in fig. 3, the first bearing mounting section 232 is used for mounting the first bearing 61 so that the first shaft body 23 can be rotatably mounted to the housing 10 through the first bearing 61. The machining accuracy of the first bearing mounting section 232 is higher than that of the first end 231. On one hand, the first bearing mounting section 232 is high in machining precision, so that stability of the first bearing 61 and the first shaft body 23 in the operation process can be guaranteed. On the other hand, the first end 231 is formed with a low machining accuracy, and the cost of the first shaft body 23 in the manufacturing process can be reduced.

In the embodiment of the present application, the diameter of the first bearing mounting section 232 is 0.5mm larger than the diameter of the first end 231, so that a step is formed between the first bearing mounting section 232 and the first end 231, thereby facilitating an operator to determine a specific boundary between the first bearing mounting section 232 and the first end 231 through the step during a subsequent mounting process.

As shown in fig. 1, a plurality of first helical blades are provided on the circumferential side surface of the first rotor 21, and a thread is formed between the plurality of first helical blades. A plurality of second spiral blades are provided on the circumferential side surface of the second rotor 22, the direction of rotation of the second spiral blades is opposite to the direction of rotation of the first spiral blades, and a screw thread is formed between the plurality of second spiral blades.

As shown in fig. 1, the first rotor 21 and the second rotor 22 may be integrally formed and then sleeved on the first rotor assembly mounting section 233 of the first shaft 23, and the first rotor 21 and the second rotor 22 are integrally formed, so that the strength of the second rotor assembly 30 may be increased. Alternatively, the first rotor 21, the second rotor 22 and the first shaft 23 are integrally formed, so that the overall strength of the first rotor assembly 20 and the first shaft 23 is further increased.

In the embodiment of the present application, since the thread direction of the first rotor 21 is opposite to the thread direction of the second rotor 22, the portion of the first rotor assembly mounting section 233 of the first shaft 23 is integrally formed with the first rotor 21, and the second rotor 22 is sleeved on the first rotor assembly 20 mounting section. On one hand, the structure that the first rotor 21 assembly is integrally formed with the first shaft body 23 enables the overall strength and coaxiality of the first rotor 21 assembly and the first shaft body 23 to be higher, so that the compressor 100 provided by the embodiment of the present application is more stable in the process of moving. On the other hand, the first rotor 21 and the second rotor 22 are manufactured separately, which reduces the difficulty and cost of manufacturing the first rotor assembly 20.

In the present embodiment, the second rotor assembly 30 may include a third rotor 31 and a fourth rotor 32 coaxially disposed as described in fig. 1 and 2. The first rotor 21 and the third rotor 31 mesh with each other, and the second rotor 22 and the fourth rotor 32 mesh with each other. It can be understood that, as shown in fig. 1 and 2, by rotating the first rotor 21 and the third rotor 31 simultaneously and rotating the second rotor 22 and the fourth rotor 32 simultaneously, air can be sucked through the air inlet 13 by the first rotor 21 and the third rotor 31, and can be discharged through the air inlet 13 by the second rotor 22 and the fourth rotor 32, and can be discharged through the first air outlet 11 by the first rotor 21 and the third rotor 31, and can be discharged through the second air outlet 12 by the second rotor 22 and the fourth rotor 32 simultaneously, so that the double increase of the air discharge amount of the compressor 100 can be realized.

As shown in fig. 1, the third rotor 31 has a plurality of third spiral blades formed on a circumferential side thereof with a screw thread therebetween and engaged with the first spiral blades. The fourth rotor 32 has a plurality of fourth screw blades formed on a circumferential side thereof, and the plurality of fourth screw blades are formed with a screw thread therebetween and engaged with the second screw blades.

Illustratively, as shown in fig. 2, the second rotor assembly 30 further includes a second shaft 33. The second shaft body 33 is used to carry the third rotor 31 and the fourth rotor 32. One end of the second shaft 33 is rotatably mounted on the housing 10 through a third bearing 63, and the other end of the second shaft 33 is rotatably mounted on the housing 10 through a fourth rotating shaft.

The third rotor 31 and the fourth rotor 32 may be integrally formed and then sleeved on the second shaft body 33. Alternatively, the third rotor 31, the fourth rotor 32 and the second shaft body 33 may be integrally formed. Alternatively, either one of the third rotor 31 and the fourth rotor 32 may be integrally formed with the second shaft body 33.

In the embodiment of the present application, since the thread directions of the third rotor 31 and the fourth rotor 32 are opposite, the third rotor 31 and the fourth rotor 32 are manufactured separately, so as to reduce the difficulty in manufacturing the second rotor assembly 30.

As shown in fig. 1, for the second rotor assembly 30 and the first rotor assembly 20, when the second rotor assembly 30 and the first rotor assembly 20 are meshed with each other and rotate together, due to the fact that the rotation directions of the first rotor 21 and the second rotor 22 are opposite, opposite axial forces can be generated, and the rotation directions of the third rotor 31 and the fourth rotor 32 are opposite, opposite axial forces can be generated, axial forces between the first rotor 21 and the second rotor 22 can be offset to some extent, and axial forces between the third rotor 31 and the fourth rotor 32 can be offset to some extent.

It should be noted, however, that in actual manufacturing processes, it is found that, on the one hand, there are manufacturing errors during the manufacturing of the second rotor assembly 30 and the first rotor assembly 20. On the other hand, there is a certain difference in the fit between the second rotor assembly 30 and the first rotor assembly 20 due to the problems of tolerance and deviation in assembly. Further, it is caused that the axial force between the first rotor 21 and the second rotor 22 cannot be completely cancelled, and the axial force between the third rotor 31 and the fourth rotor 32 cannot be completely cancelled. Therefore, it is not possible to achieve almost complete cancellation of the axial force when the second rotor assembly 30 and the second rotor assembly 30 are meshed with each other to rotate together. As a result, the second rotor assembly 30 and the first rotor assembly 20 will produce a resultant of randomly directed axial forces when rotating.

In the prior 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 the second shaft body 33 and the first shaft body 23 of the compressor 100 to limit the resultant axial force of the second rotor assembly 30 and the first rotor assembly 20 in all the molded compressors 100, so as to ensure that the compressor 100 can stably operate. The compressor 100 of the prior art is therefore cost effective, with the attendant excess mechanical losses and lubricant requirements, and increases the failure rate of the compressor 100. Finally, the size and the cost of the compressor 100 assembly are increased, the mechanical efficiency of shafting operation is reduced to a certain extent, and the requirement of lubricating oil quantity is increased.

In this regard, the embodiments of the present application ensure that the second rotor assembly 30 and the first rotor assembly 20 have a defined resultant axial force in a single axial direction when the second rotor assembly 30 and the first rotor assembly 20 of the compressor 100 are meshed with each other for rotation. Therefore, the first thrust bearing is only required to be arranged on one shaft body, such as the second shaft body 33, so as to limit the resultant axial force in the determined single axial direction, and the second rotor assembly 30 and the first rotor assembly 20 of the compressor 100 of the embodiment of the present invention can be ensured to stably rotate without causing the second rotor assembly 30 and the first rotor assembly 20 to contact and rub with the end surface of the shell 10. Compared with the technical scheme before improvement that two thrust bearings are required to be fixed on one shaft body, the compressor 100 of the embodiment of the application can save a plurality of thrust bearings, and the overall size and cost of the compressor 100 can be reduced. Meanwhile, due to the reduction of the number of the thrust bearings, the efficiency of shafting operation can be improved to a certain degree, and the requirement of lubricating oil quantity is reduced.

In the embodiment of the present application, by designing the internal configuration of the compressor 100 to be a preset difference during the production process of the compressor 100, it can be ensured that the compressor 100 generates a directionally determined and uniquely directed resultant axial force between the second rotor assembly 30 and the first rotor assembly 20.

The following description is made in terms of the shape of the second and second rotor assemblies 30 and 30 used in the compressor 100, and the difference in the shape of the second and second rotor assemblies 30 and 30, which results in the difference in the gas force.

In the embodiment of the present application, the first and third rotors 21 and 31 have different shapes from the second and fourth rotors 22 and 32 to generate a difference in gas force during the rotation of the second and second rotor assemblies 30 and 30 to form a predetermined force applied to the first thrust bearing. It is understood that the shape of the first rotor 21 is different from the shape of the second rotor 22 and the fourth rotor 32; and/or the third rotor 31 may have a different shape from the second and fourth rotors 22 and 32 to generate a pressure difference to form a predetermined force during the rotation of the second and fourth rotor assemblies 30 and 30.

The shape of the first and third rotors 21 and 31 different from the shape of the second and fourth rotors 22 and 32 includes, but is not limited to: the shape of the first rotor 21 is different from that of the second rotor 22, and the shape of the third rotor 31 is different from that of the fourth rotor 32; the shape of the first rotor 21 is different from that of the second rotor 22, and the shape of the third rotor 31 is the same as that of the fourth rotor 32; the shape of the first rotor 21 is the same as that of the second rotor 22, and the shape of the third rotor 31 is different from that of the fourth rotor 32; the shape of the first rotor 21 is different from that of the fourth rotor 32, and the shape of the third rotor 31 is different from that of the fourth rotor 32; the shape of the first rotor 21 is different from that of the fourth rotor 32, and the shape of the third rotor 31 is the same as that of the fourth rotor 32; the shape of the first rotor 21 is the same as that of the fourth rotor 32, and the shape of the third rotor 31 is different from that of the fourth rotor 32; the shape of the first rotor 21 is different from that of the fourth rotor 32, and the shape of the third rotor 31 is the same as that of the second rotor 22; the shape of the first rotor 21 is different from that of the fourth rotor 32, and the shape of the third rotor 31 is different from that of the second rotor 22; the shape of the first rotor 21 is the same as that of the fourth rotor 32, and the shape of the third rotor 31 is different from that of the second rotor 22; the shape of the first rotor 21 is different from that of the fourth rotor 32, and the shape of the third rotor 31 is the same as that of the fourth rotor 32.

Further, the shape of the first rotor 21 and the third rotor 31 different from the shape of the second rotor 22 and the fourth rotor 32 includes, but is not limited to: the first rotor 21, the second rotor 22, the third rotor 31, and the fourth rotor 32 have any one of a length, an angle of the spiral blades, an end surface profile, a density of the spiral blades, and a diameter. It will be appreciated that the shape of the first and third rotors 21, 31 being different from the shape of the second and fourth rotors 22, 32 includes, but is not limited to: the first rotor 21, the second rotor 22, the third rotor 31, and the fourth rotor 32 have any one of a length, an angle of the spiral blades, an end surface profile, a density of the spiral blades, and a diameter.

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 compressor and the air conditioner provided by the embodiments of the present application are described in detail above, and the principles and embodiments of the present application are explained herein by applying specific examples, and the description of the above embodiments is only used to help understand the method and the core idea of the present application; meanwhile, for those skilled in the art, according to the idea of the present application, 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 application.

Claims (10)

1. A compressor, comprising:

the first rotor assembly comprises a first rotor, a second rotor and a first shaft body, the first rotor and the second rotor are coaxially arranged, the thread turning directions are opposite, the first shaft body bears and drives the first rotor and the second rotor to rotate, the first shaft body comprises a first end located in the axial direction of the first shaft body, and the first end is provided with a flat position for transmission; and

the second rotor assembly comprises a third rotor and a fourth rotor which are coaxially arranged, the third rotor is meshed with the first rotor, and the fourth rotor is meshed with the second rotor.

2. The compressor of claim 1, wherein the flat portion is provided in plurality, and the plurality of flat portions are uniformly provided in a circumferential direction of the first shaft body.

3. The compressor of claim 2, wherein an arc surface is formed between two adjacent flat positions.

4. The compressor of claim 1, wherein the flat portion has a first driving plane parallel to an axial direction of the first shaft body and a thrust surface perpendicularly connected to the first driving plane, the thrust surface being located on a side of the first driving plane adjacent to the first rotor.

5. The compressor of claim 4, wherein the ratio of the distance from the first drive plane to the first end axis to the first end radius is A, wherein A is 0.75 ≦ 0.85.

6. The compressor of claim 4, further comprising a motor having a motor rotor with a mounting hole, wherein the first end portion is disposed in the mounting hole, and wherein a sidewall forming the mounting hole is provided with a second driving plane conforming to the first driving plane.

7. The compressor of claim 6, wherein the first end has a first end face at an axial end of the first shaft, the first end face being perpendicularly connected to the first drive plane, the first end face being provided with a lock member, the motor rotor being interposed between the lock member and the thrust surface.

8. The compressor of any one of claims 1-7, wherein the first shaft body has a first bearing mount section coupled to the first end, the first bearing mount section machined to a different precision than the first end.

9. The compressor of claim 8, wherein the first end is not equal in diameter to the first bearing mounting section.

10. An air conditioner characterized by comprising a compressor according to any one of claims 1 to 9.

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