CN113606139A

CN113606139A - Compressor and shutdown method thereof, and air conditioner

Info

Publication number: CN113606139A
Application number: CN202110902622.3A
Authority: CN
Inventors: 孟强军; 武晓昆; 龙忠铿; 毕雨时
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2021-08-06
Filing date: 2021-08-06
Publication date: 2021-11-05

Abstract

The present application provides a compressor, a shutdown method thereof, and an air conditioner. The compressor includes a rotor assembly, including a first rotating shaft and a first rotor. The first rotor is coaxially connected to the first rotating shaft and has opposite screw threads. The first working part and the second working part, the first working part and the second working part can rotate along the first axis, when the first working part and the second working part are along the first When the axis rotates, an axial force along the first axis direction is generated; the magnetic force assembly includes a first magnetic part, and the first magnetic part is used for generating a first axial force along the first axis direction before the compressor is shut down. a magnetic force. The first magnetic element of the present application generates a first magnetic force along the first axis direction before the compressor is shut down, so that the resultant force of the first magnetic force and the axial force along the first axis faces a preset direction or is 0 during the shutdown process of the compressor, It avoids the influence of the change of the axial force direction on the rotor work during the shutdown process of the compressor.

Description

Compressor, shutdown method thereof and air conditioner

Technical Field

The application relates to the technical field of compressors, in particular to a compressor, a shutdown method of the compressor and an air conditioner.

Background

At present, the screw compressor has the characteristics of small size, light weight, easy maintenance and the like, is mainly applied to compressed air and medium-sized refrigeration heat pump air-conditioning systems, and gradually replaces a reciprocating compressor within a medium refrigerating capacity range due to the continuous improvement of the working reliability of the screw compressor and occupies part of the market of a centrifugal compressor.

In the related art, the screw compressor has two pairs of rotors meshed with each other, two sets of working parts meshed with each other are arranged on the two rotors, the two sets of working parts respectively convey compressed media from two sides together, the displacement of the compressor is improved, and meanwhile, the two sets of working parts convey the compressed media together, so that axial forces generated by the two sets of working parts are offset mutually. However, the unstable flow is easily generated during the shutdown process of the compressor, and further the axial force generated by the two sets of working parts of the two rotors fluctuates in magnitude and even changes in direction, so that the axial force of the two rotors needs to be limited during the actual processing and assembling processes of the screw compressor, for example, the axial force limitation during the shutdown process of the compressor is performed by providing thrust bearings at the two ends of the two rotors, and this results in the increase of the overall size and cost of the compressor.

Disclosure of Invention

The application provides a compressor, a shutdown method thereof and an air conditioner, and aims to solve the technical problem that axial force fluctuates and even the direction changes in the shutdown process of the conventional screw compressor.

In a first aspect, the present application provides a compressor comprising:

the rotor assembly comprises a first rotating shaft and a first rotor, wherein the first rotor is provided with a first working part and a second working part which are coaxially connected with the first rotating shaft and have opposite thread turning directions, the first working part and the second working part can rotate along a first axis, and when the first working part and the second working part rotate along the first axis, an axial force in the direction of the first axis is generated;

the magnetic assembly comprises a first magnetic part, and the first magnetic part is used for generating a first magnetic force along the first axial direction before the compressor is shut down, so that the resultant force of the first magnetic force and the axial force in the shutdown process of the compressor faces to a preset direction or is 0 along the first axis.

In some embodiments, the magnetic assembly further includes a second magnetic member for generating a second magnetic force having the same direction as the first magnetic force when the compressor is in the operating state.

In some embodiments, the first magnetic member and the second magnetic member are located at the same end of the first rotating shaft; or

The first magnetic part and the second magnetic part are positioned at two opposite ends of the first rotating shaft.

In some embodiments, the second magnetic member includes a driving motor coupled to the first rotating shaft, the driving motor configured to generate a second magnetic force having the same direction as the first magnetic force.

In some embodiments, the driving motor comprises a motor stator and a motor rotor which are arranged at intervals, and the motor rotor is connected with the first rotating shaft;

the motor stator comprises a first end face, the motor rotor comprises a second end face located on the same side with the first end face, and the first end face and the second end face are arranged in a staggered mode along the axial direction of the first rotating shaft.

In some embodiments, the distance between the first end surface and the rotor assembly is greater than the distance between the second end surface and the rotor assembly, and the second magnetic member is disposed at the same end of the first rotating shaft as the first magnetic member; or

The distance between the first end face and the rotor assembly is smaller than that between the second end face and the rotor assembly, and the second magnetic part is arranged at one end, deviating from the first magnetic part, of the first rotating shaft.

In some embodiments, the first magnetic member is located at an end of the first shaft proximate to the drive motor, and the drive motor further includes a shield surrounding the motor stator and the motor rotor.

In some embodiments, the magnetic switch further comprises a detection component, wherein the detection component is used for detecting the rotating speed of the first rotating shaft so as to switch on or switch off the first magnetic part or control the input power of the first magnetic part according to the rotating speed of the first rotating shaft.

In some embodiments, the axial force limiter is disposed at one end of the first rotating shaft and is configured to generate an axial thrust force that counteracts a resultant force of the first magnetic force or the second magnetic force and the axial force.

In some embodiments, the rotor assembly further includes a second rotor having a first sub-working portion in meshing engagement with the first working portion, and a second sub-working portion in meshing engagement with the second working portion.

In a second aspect, the present application provides a compressor shutdown method, which is applied to the compressor according to the first aspect, and includes:

the first magnetic piece is started before the compressor is shut down, and generates a first magnetic force along the first axial direction;

and closing the compressor to stop providing power for the rotor assembly, wherein the resultant force of the axial force generated by rotation of the rotor assembly in the shutdown process and the first magnetic force is towards the preset direction or 0 along the first axis.

In some embodiments, prior to the step of turning on the first magnetic member, the method further comprises:

acquiring rotating speed information of the rotor assembly;

calculating the rotating speed change rate of the rotor assembly according to the rotating speed information;

and when the rotating speed change rate is less than or equal to the preset rotating speed change rate, the first magnetic piece is started.

In some embodiments, the rotation speed information includes a first rotation speed and a second rotation speed of the rotor assembly spaced apart by a preset time, and the step of calculating the rotation speed change rate of the rotor assembly according to the rotation speed information includes:

and calculating the rotating speed change rate according to the first rotating speed, the second rotating speed and the preset time.

In some embodiments, after shutting down the compressor to stop providing power to the rotor assembly, the method further comprises:

acquiring the rotating speed of the rotor assembly;

and when the rotating speed is less than or equal to the preset rotating speed, closing the first magnetic piece.

In some embodiments, the step of turning on the first magnetic member comprises:

acquiring the rotating speed of the rotor assembly;

and determining the input power to the first magnetic member according to the rotating speed of the rotor assembly so as to control the magnitude of the first magnetic force.

In some embodiments, after the step of turning on the first magnetic member, the method further comprises:

acquiring rotating speed information of the rotor assembly;

and determining the change rate of the input power of the first magnetic member according to the change rate of the rotating speed so as to reduce the first magnetic force along with the reduction of the rotating speed of the rotor assembly in the shutdown process of the compressor.

In a third aspect, the present application provides an air conditioner comprising a compressor as described in the first aspect.

According to the magnetic component, the first magnetic component is arranged in the screw compressor, and the first magnetic component generates the first magnetic force along the direction of the first axis before the compressor is shut down, so that the resultant force of the first magnetic force and the axial force in the shutdown process of the compressor is towards the preset direction or 0 along the first axis, the rotor only receives the resultant force action in a single direction in the shutdown process of the compressor, and finally the influence on the work of the rotor due to the change of the direction of the axial force in the shutdown process of the compressor is avoided.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.

FIG. 1 is a schematic view of a compressor configuration provided in an embodiment of the present application;

FIG. 2 is a schematic view of another configuration of a compressor provided in an embodiment of the present application;

fig. 3 is a schematic structural view of a second magnetic member provided in the embodiment of the present application;

FIG. 4 is a schematic view of another configuration of a compressor provided in an embodiment of the present application;

fig. 5 is another structural schematic view of the second magnetic member provided in the embodiment of the present application;

FIG. 6 is a schematic flow chart of a compressor shutdown method provided in an embodiment of the present application;

fig. 7 is a schematic flow chart of the method for opening the first magnetic member provided in the embodiment of the present application;

FIG. 8 is a schematic flow chart of the closing of the first magnetic member provided in the embodiments of the present application;

fig. 9 is a schematic flow chart of controlling the initial input power of the first magnetic member provided in the embodiment of the present application;

fig. 10 is a schematic flow chart of controlling the initial input power of the first magnetic member provided in the embodiment of the present application.

Wherein, 10 rotor assemblies, 11 first rotating shafts, 12 second rotating shafts, 13 first rotors, 14 second rotors, 15 first axes, 16 second axes;

131 a first working part, 132 a second working part, 141 a first sub-working part, 142 a second sub-working part;

20 a magnetic assembly, 21 a first magnetic member, 22 a second magnetic member;

221 driving motor, 2211 motor stator, 2212 motor rotor, 222 detection component, 210 first end face and 220 second end face;

30 axial force limiters, 40 chock;

f axial force, F1 first magnetic force, F2 second magnetic force, F0 total force.

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, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the 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 invention.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be considered as limiting the present invention. Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, features defined as "first", "second", may explicitly or implicitly include one or more of the described features. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.

In this application, the word "exemplary" is used to mean "serving as an example, instance, or illustration. Any embodiment described herein as "exemplary" is not necessarily to be construed as preferred or advantageous over other embodiments. The following description is presented to enable any person skilled in the art to make and use the invention. In the following description, details are set forth for the purpose of explanation. It will be apparent to one of ordinary skill in the art that the present invention may be practiced without these specific details. In other instances, well-known structures and processes are not shown in detail to avoid obscuring the description of the invention with unnecessary detail. Thus, the present invention is not intended to be limited to the embodiments shown, but is to be accorded the widest scope consistent with the principles and features disclosed herein.

At present, thrust bearings are needed to be adopted at two sides of a rotating shaft for the axial force fluctuation phenomenon of the screw compressor so as to prevent the rotor from being damaged due to the fact that the side face of the rotor impacts a shell or other parts.

In view of the above, the inventor of the present invention has found that, by arranging the rotor and the stator of the compressor motor in an offset manner, because the motor stator and the motor rotor are misaligned in the axial direction, the pulling direction of the main electromagnetic force is not only perpendicular to the axial direction of the first rotating shaft, but is arranged in an inclined manner with respect to the axial direction of the first rotating shaft, that is, the inclined direction of the main electromagnetic force faces the side opposite to the axial offset direction of the motor rotor, so that the axial force F of the screw compressor can be oriented by the magnetic force of the motor.

However, the inventor of the present invention has found that, in the case of a non-permanent-magnet motor, the main electromagnetic force needs to be ensured when the motor is energized, and therefore, the axial force F fluctuates in magnitude and changes in direction during the shutdown process of the screw compressor; meanwhile, if other magnetic parts are simultaneously started at the moment of shutdown, the magnetic force of the motor disappears and the magnetic force of other magnetic parts does not act on the rotor, for example, the electromagnet needs to generate magnetic force only after being electrified for a short time, and the axial force F suddenly loses the magnetic force limitation of the motor, which causes the rotor to lose control instantly and further generates the phenomenon of collision damage.

Referring first to fig. 1, fig. 1 shows a schematic structural diagram of a compressor in an embodiment of the present application, wherein the compressor includes:

a rotor assembly 10 including a first rotating shaft 11 and a first rotor 13, the first rotor 13 having a first working portion 131 and a second working portion 132 coaxially connected with the first rotating shaft 11 and having opposite thread directions, the first working portion 131 and the second working portion 132 being capable of rotating along a first axis 15, and generating an axial force F in the direction of the first axis 15 when the first working portion 131 and the second working portion 132 rotate along the first axis 15;

the magnetic assembly 20 comprises a first magnetic member 21, and the first magnetic member 21 is configured to generate a first magnetic force F1 in a direction along the first axis 15 before the compressor is turned off, so that a resultant force F0 of the first magnetic force F1 and the axial force F is directed towards a preset direction or 0 along the first axis 15 during the turning off of the compressor.

It should be noted that, during the operation of the compressor of the present invention, when the first working portion 131 and the second working portion 132 rotate along the first axis 15, an axial force F along the first axis 15 is generated, the first axis 15 is the axial direction of the first rotating shaft 11, and due to the difference existing during the actual machining and assembling processes of the first working portion 131 and the second working portion 132, the configurations of the first working portion 131 and the second working portion 132 cannot be completely the same, and therefore, the direction of the axial force F is uncertain.

According to the screw compressor, the first magnetic piece 21 is arranged in the screw compressor, and the first magnetic piece 21 generates the first magnetic force F1 along the direction of the first axis 15 before the compressor is shut down, so that the resultant force F0 of the first magnetic force F1 and the axial force F faces the preset direction or is 0 along the first axis 15 in the shutdown process of the compressor, the rotor is only acted by the resultant force F0 in a single direction, and the influence on the work of the rotor due to the change of the direction of the axial force F in the shutdown process of the compressor is avoided. Meanwhile, the rotor pair is only subjected to the action of the resultant force F0 in a single direction, and in order to counteract the action of the resultant force F0, the normal operation of the rotor pair can be ensured only by arranging the axial force limiting piece 30 on one side of the first rotating shaft 11, and the axial force limiting pieces 30 do not need to be arranged at two ends of the first rotating shaft 11 and the second rotating shaft 12, so that the overall size of the compressor is reduced, and the manufacturing cost of the compressor is reduced.

Specifically, the rotor assembly 10 is a working assembly that transports fluid by rotating at least one rotor, wherein the rotor assembly 10 includes at least a first rotor 13. To better counteract the two axial forces F generated by the first rotor 13, in some embodiments of the present invention, the first working portion 131 transports fluid in a first direction and the second working portion 132 transports fluid in a second direction, wherein the first and second directions are opposite directions.

As an example, as shown in fig. 1, the fluid enters the first rotor 13 from the middle between the first working portion 131 and the second working portion 132 of the first rotor 13, the first working portion 131 conveys the fluid to the left, the second working portion 132 conveys the fluid to the right, and since the directions of conveying the fluids are opposite, two axial forces F generated by the first rotor 13 are both along the axial direction of the first rotor 13, and at the same time, the directions of the two axial forces F are both directed to the middle of the first rotor 13, so that the two axial forces F generated by the first rotor 13 are offset to the middle.

In order to cause the first working portion 131 of the first rotor 13 to deliver fluid to the left, the second working portion 132 of the first rotor 13 delivers fluid to the right, as an example, the first working portion 131 has right-handed helical blades, the second working portion 132 has left-handed helical blades, and the direction of rotation of the first rotor 13 is counterclockwise. In operation, the first rotor 13 rotates counterclockwise, and since the first working portion 131 has right-handed helical blades, it can be determined that the first working portion 131 is matched to deliver fluid to the left according to the right-handed rule and the left-handed rule for determining the fluid delivery direction, and conversely, the second working portion 132 delivers fluid to the right.

As another example, the first working portion 131 has a left-handed helical lobe, the second working portion 132 has a right-handed helical lobe, and the direction of rotation of the first rotor 13 is clockwise. In operation, the first rotor 13 rotates clockwise, and since the first working portion 131 has helical lobes with left-handed rotation, it can be determined that the first working portion 131 delivers fluid to the left according to the right-handed rule and the left-handed rule for determining the fluid delivery direction, whereas the second working portion 132 delivers fluid to the right.

It will be appreciated that the fluid also flows in from the two ends of the first rotor 13 and then out of the first working portion 131 and the second working portion 132, respectively, also for the purpose of counteracting the two axial forces F generated by the first rotor 13 towards the middle.

The magnetic assembly 20 is used to generate a magnetic force to balance the axial force F generated by the rotor assembly 10. The magnetic assembly 20 includes a first magnetic member 21, and the first magnetic member 21 is configured to generate a first magnetic force F1 along the first axis 15 before the compressor is turned off, so that a resultant force F0 of the first magnetic force F1 and the axial force F is toward a predetermined direction or 0 along the first axis 15 during the turning off of the compressor. Specifically, the first magnetic member 21 may be a magnet or an electromagnet, and the first magnetic force F1 along the first axis 15 is generated by a magnetic force of the magnet or an electromagnetic force of the electromagnet. For example, the first magnetic member 21 may be fixed to other components of the compressor, for example, referring to fig. 2, the first magnetic member 21 may be fixed to the bearing end cap.

In order to achieve the balance of the axial force F during the operation of the compressor, the magnetic assembly 20 further includes a second magnetic member 22, and the second magnetic member 22 is configured to generate a second magnetic force F2 having the same direction as the first magnetic force F1 when the compressor is in the operation state, so as to ensure the balance of the axial force F during the operation state or the shutdown state of the compressor.

In some embodiments of the present application, the first magnetic member 21 and the second magnetic member 22 may be located at the same end of the first rotating shaft 11, that is, both the magnetic forces provided by the first magnetic member 21 and the second magnetic member 22 are attraction forces or repulsion forces, for example, as shown in fig. 1, both the first magnetic member 21 and the second magnetic member 22 are located at the left end of the first rotating shaft 11, and both the magnetic forces provided by the first magnetic member 21 and the second magnetic member 22 are attraction forces, so that the resultant force F0 of the axial force F and the magnetic force is always to the left when the compressor is in an operating state or is turned off.

In other embodiments of the present application, the first magnetic member 21 and the second magnetic member 22 may be located at opposite ends of the first rotating shaft 11, and the magnetic forces provided by the first magnetic member 21 and the second magnetic member 22 are an attractive force and a repulsive force. For example, as shown in fig. 2, fig. 2 shows another structural schematic diagram of the compressor in the embodiment of the present application, the first magnetic member 21 is located at the right end of the first rotating shaft 11, the second magnetic member 22 is located at the left end of the first rotating shaft 11, the magnetic force provided by the first magnetic member 21 is a repulsive force, and the magnetic force provided by the second magnetic member 22 is an attractive force, so that the resultant force F0 of the axial force F and the magnetic force is always to the left when the compressor is in an operating state or is turned off.

Specifically, the second magnetic member 22 includes a driving motor 221, the driving motor 221 is connected to the first rotating shaft 11, and the driving motor 221 is configured to generate a second magnetic force F2 having the same direction as the first magnetic force F1, so as to achieve the purpose of providing the second magnetic force F2 while driving the first rotating shaft 11 to rotate, without adding an additional magnetic structure in the compressor, so as to reduce the manufacturing cost of the compressor.

Specifically, referring to fig. 1 to 5, fig. 3 shows a schematic structural diagram of the second magnetic member 22 in fig. 2, fig. 4 shows another schematic structural diagram of a compressor in an embodiment of the present application, and fig. 4 shows a schematic structural diagram of the second magnetic member 22 in fig. 3, wherein the driving motor 221 includes a motor stator 2211 and a motor rotor 2212 which are arranged at intervals, and the motor rotor 2212 is connected to the first rotating shaft 11.

The motor stator 2211 includes a first end surface 210, the motor rotor 2212 includes a second end surface 220 located on the same side as the first end surface 210, and the first end surface 210 and the second end surface 220 are disposed in a staggered manner along the axial direction of the first rotating shaft 11. The compressor provided by the embodiment of the invention generates the second magnetic force F2 by axially displacing the first end face 210 of the motor stator 2211 and the second end face 220 of the motor rotor 2212, that is, the second magnetic force F2 can be generated by simply modifying the structure of the driving motor 221, so that the cost can be reduced.

In this embodiment, when a closed magnetic circuit is formed between motor stator 2211 and motor rotor 2212, motor rotor 2212 as a current-carrying conductor is pulled by the main electromagnetic force, and because motor stator 2211 and motor rotor 2212 are axially misaligned, the pulling direction of the main electromagnetic force is no longer perpendicular to the axial direction of first rotating shaft 11, i.e. is inclined from the axial direction of first rotating shaft 11, i.e. the inclined direction of the main electromagnetic force faces the side opposite to the axial direction of motor rotor 2212. For example, if motor rotor 2212 is axially shifted to the right, the inclination direction of the main electromagnetic force is to the left. Therefore, the main electromagnetic force may resolve an electromagnetic force along the first axis 15 and a radial electromagnetic force along the radial direction of the first rotating shaft 11, the radial electromagnetic force drives the first rotating shaft 11 to rotate, and the electromagnetic force along the first axis 15 is the second magnetic force F2 along the first axis 15.

Further, in order to avoid the situation that the magnetic member is required to be arranged on the first rotating shaft 11 so that the second magnetic member 22 generates the repulsive force to act on the rotor assembly 10, the first magnetic member 21 generates the attractive force to act on the first rotor 13 made of the metal material, so as to realize the balance of the axial force F.

As an exemplary embodiment of generating an attractive force to the first magnetic element 21 to act on the rotor assembly 10 to achieve balance of the axial force F, referring to fig. 1 and fig. 3, a distance between the first end surface 210 and the rotor assembly 10 is greater than a distance between the second end surface 220 and the rotor assembly 10, the second magnetic element 22 is disposed at an end of the first rotating shaft 11 that is the same as the first magnetic element 21, that is, the motor stator 2211 is far away from the rotor assembly 10 relative to the motor rotor 2212, so that an inclination direction of a main electromagnetic force of the motor faces to the left, and the second magnetic element 22 and the first magnetic element 21 are located at the same side and both act as an attractive force, so that a resultant force F0 of the axial force F and the magnetic force is always applied to the left side in an operating state or shutdown of the compressor.

As another exemplary embodiment for generating an attractive force to the first magnetic member 21 to act on the rotor assembly 10 to achieve balance of the axial force F, referring to fig. 4 and fig. 5, a distance between the first end surface 210 and the rotor assembly 10 is smaller than a distance between the second end surface 220 and the rotor assembly 10, the second magnetic member 22 is disposed at an end of the first rotating shaft 11 away from the first magnetic member 21, that is, the motor stator 2211 is close to the rotor assembly 10 relative to the motor rotor 2212, so that an inclination direction of a main electromagnetic force of the motor faces right, the second magnetic member 22 and the first magnetic member 21 are respectively located at two ends of the first rotating shaft 11, wherein a magnetic force of the second magnetic member 22 acts as a repulsive force, and a magnetic force of the first magnetic member 21 acts as an attractive force, so that a resultant force F0 of the axial force F and the magnetic force is always directed right when the compressor is in an operating state or is turned off.

Further, the size of the gap L between the first end surface 210 and the second end surface 220 is in positive correlation with the size of the second magnetic force F2. The larger or smaller the offset distance L between the first end face 210 and the second end face 220, the larger or smaller the second magnetic force F2. The compressor controls the size of the second magnetic force F2 by controlling the size of the staggered distance L, and is beneficial to ensuring that the resultant force F0 of the axial force F and the second magnetic force F2 faces to a preset direction.

In some embodiments of the present application, for example, for the embodiment where the second magnetic member 22 and the first magnetic member 21 are located at the same end of the first rotating shaft 11, in order to avoid the magnetic field of the first magnetic member 21 from affecting the driving motor 221, the driving motor 221 further includes a shielding device surrounding the motor stator 2211 and the motor rotor 2212, for example, a shielding case with a function of shielding the magnetic field, and the shielding device can shield the magnetic field of the first magnetic member 21 to ensure the normal operation of the driving motor 221.

In order to facilitate turning on and off the first magnetic member 21 or controlling the input power of the first magnetic member 21 to control the magnitude of the first magnetic force F1 of the first magnetic member 21, referring to fig. 1, in some embodiments of the present application, the compressor further includes a detecting component 222, and the detecting component 222 is configured to detect the rotation speed of the first rotating shaft 11 to turn on and off the first magnetic member 21 or control the input power of the first magnetic member 21 according to the rotation speed of the first rotating shaft 11. Specifically, the detecting component 222 may be disposed at the driving motor 221 so as to detect the rotation speed of the first rotation shaft 11, for example, the detecting component 222 may include an optical code disc disposed at the driving motor 221 so as to detect the rotation speed of the first rotation shaft 11 through an optical grating of the optical code disc.

It is understood that the detecting component 222 can also be a sensor, such as a photoelectric type rotation speed sensor, a variable reluctance type rotation speed sensor, a capacitance type rotation speed sensor, a hall rotation speed sensor, etc.

In some embodiments of the present invention, to facilitate balancing the axial force F generated by the rotor assembly 10, the rotor assembly 10 further includes an axial force limiter 30, and the axial force limiter 30 is connected to the first rotating shaft 11 and is used for counteracting the resultant force F0 in a preset direction generated by the rotor assembly 10 during operation.

Illustratively, the axial force limiter 30 may be a thrust bearing, such as: angular contact ball bearings, thrust ball bearings, cylindrical thrust roller bearings, needle thrust bearings, tapered thrust roller bearings, self-aligning thrust roller bearings, and the like. A particular axial force limiter 30 may be secured to a bearing seat 40 as shown in fig. 1. It is understood that the axial force limiter 30 may be other working members capable of counteracting the action of the axial force F, such as a balance drum, a balance disc, etc.

As an example, as shown in fig. 2, the axial force limiter 30 may include only a thrust bearing provided on the first rotating shaft 11, and the resultant force F0 in the preset direction is cancelled by the thrust bearing rotatably connected to the first rotating shaft 11. For example, the thrust bearing may be located at an end of the first rotating shaft 11 opposite to the predetermined direction, as shown in fig. 2, the axial force limiting member 30 is disposed at the right end of the first rotating shaft 11, and since the resultant force F0 between the axial force F of the rotor assembly 10 and the first magnetic force F1 or the second magnetic force F2 is towards the left, the thrust bearing disposed at the right end of the first rotating shaft 11 may pull the first rotating shaft 11 to the right, so that the rotor assembly 10 is forced to be 0 as a whole, and the normal operation of the rotor assembly 10 is ensured. It is understood that the thrust bearing may be disposed at an end of the first rotating shaft 11 that is the same as the predetermined direction, for example, a left end of the first rotating shaft 11 as shown in fig. 2.

To achieve better compression and delivery of the gas, in some embodiments of the invention, the rotor assembly 10 may further include a second rotor 14, the second rotor 14 being rotatable about a second axis 16. Specifically, the second rotor 14 is engaged with the first rotor 13, the second rotor 14 has a first sub-working portion 141 and a second sub-working portion 142, the first sub-working portion 141 is engaged with the first working portion 131 and is spirally oppositely disposed, and the second sub-working portion 142 is engaged with the second working portion 132 and is spirally oppositely disposed.

During operation, the first rotor 13 drives the second rotor 14 to rotate, the first sub-working portion 141 and the first working portion 131 form a pair of working portions for conveying fluid, the second sub-working portion 142 and the second working portion 132 form another pair of working portions for conveying fluid, the first working portion 131 and the first sub-working portion 141 which are arranged in opposite spiral directions generate an axial force F, the second working portion 132 and the second sub-working portion 142 which are arranged in opposite spiral directions generate another axial force F which is opposite to the axial force F, and the two axial forces F are mutually offset, so that the axial force F is approximately balanced when the rotor assembly 10 comprises two rotors.

It will be appreciated that when the rotor assembly 10 includes the first rotor 13 and the second rotor 14, in order to better counteract the two axial forces F generated by the first rotor 13 and the second rotor 14, the first working portion 131 cooperates with the first sub-working portion 141 to convey fluid in a first direction, and the second working portion 132 cooperates with the second sub-working portion 142 to convey fluid in a second direction, the first direction and the second direction being opposite directions. In order to realize the flow in the opposite direction, the flow can be realized by setting the spiral directions of the first working portion 131 and the second working portion 132 on the first rotor 13, specifically, refer to the descriptions of some other embodiments of the present application, and are not described herein again.

In some embodiments of the present invention, the first rotor 13 may be fitted to the first rotating shaft 11 by fitting, for example, by key connection; in other embodiments of the present invention, the first rotor 13 may be formed integrally with the first shaft 11 in whole or in part, for example, the first working portion 131 is formed integrally with the first shaft 11, the second working portion 132 is assembled with the first shaft 11 for cooperation, and for example, the first working portion 131 and the second working portion 132 of the first rotor 13 are formed integrally with the first shaft 11. It is understood that all or part of the second rotor 14 may be integrally formed with the second rotating shaft 12, or the second rotor 14 may be assembled to the second rotating shaft 12, which is not described herein again.

In some embodiments of the present invention, for example, for the embodiment where the axial force limiter 30 only includes the thrust bearing disposed on the first rotating shaft 11, the first rotating shaft 11 drives the first rotor 13 to rotate, the second rotor 14 engaged with the first rotor 13 rotates around the second rotating shaft 12, and since the second rotor 14 is a driven member and the thrust bearing is not applied to the second rotating shaft 12, a non-metal material such as a peek material may be used for the second rotor 14 to avoid the second rotor 14 from colliding with the compressor housing or other components to cause damage.

It will be appreciated that the axial force limitation 30 may also be provided on both the first rotating shaft 11 and the second rotating shaft 12, and the effect of the resultant force F0 formed by the plurality of acting forces in the preset direction may be counteracted by the two thrust bearings.

It should be noted that the above description of the compressor is only for the purpose of clearly explaining the verification process of the present invention, and those skilled in the art can make equivalent modifications to the above compressor under the guidance of the present invention, for example, the axial force limitation 30 can also be provided at the same end of the first rotating shaft 11 and the second rotating shaft 12, and the balance of the axial force F of the rotor assembly 10 can be better achieved by two axial force limitation 30.

Further, for a better embodiment of the compressor in the present application, fig. 6 shows a flowchart of a compressor shutdown method, and fig. 6 further provides a compressor shutdown method in an embodiment of the present invention, which is applied to the compressor of any of the above embodiments, based on the compressor, where the compressor shutdown method includes:

step S601, turning on the first magnetic member 21 before the compressor is turned off, wherein the first magnetic member 21 generates a first magnetic force F1 along the first axis 15;

step S602, the compressor is turned off to stop providing power to the rotor assembly 10, and a resultant force F0 between the axial force F generated by the rotation of the rotor assembly 10 during the shutdown process and the first magnetic force F1 is directed toward the preset direction or 0 along the first axis 15.

In some embodiments of the present application, such as for embodiments in which the first magnetic member 21 is an electromagnet, turning on the first magnetic member 21 may be energizing the electromagnet such that it generates the first magnetic force F1 in the direction of the first axis 15. In other embodiments of the present application, for example, for the embodiment where the first magnetic member 21 is a magnet, the opening of the first magnetic member 21 may be to rotate the magnet structure to face the first rotating shaft 11 to generate the first magnetic force F1 along the first axis 15.

Since the first magnetic member 21 is turned on before the shutdown, at the moment when the compressor is turned off to stop providing power to the rotor assembly 10, the resultant force F0 between the axial force F generated by the rotation of the rotor assembly 10 during the shutdown process and the first magnetic force F1 faces the preset direction or is 0 along the first axis 15, so that the rotor clash damage caused by the fluctuation of the axial force F at the moment of the shutdown can be avoided. Specifically, the first magnetic member 21 can be turned on in advance by a circuit arrangement, for example, a delay circuit can be arranged to delay turning off the compressor.

In other embodiments of the present application, in order to avoid a phenomenon that the compressor is abnormally shut down when the shutdown instruction is not received due to abnormal power outage, so that the first magnetic member 21 is not timely turned on in the abnormal power outage shutdown condition, referring to fig. 7, fig. 7 shows a schematic flow chart of turning on the first magnetic member 21 in an embodiment of the present application, where before the step of turning on the first magnetic member 21, the compressor shutdown method further includes:

step S701, obtaining rotation speed information of the rotor assembly 10;

step S702, calculating a rotation speed change rate of the rotor assembly 10 according to the rotation speed information;

in step S703, when the rate of change of the rotation speed is less than or equal to the predetermined rate of change of the rotation speed, the first magnetic member 21 is turned on.

Specifically, the rotation speed information refers to rotation speed information of one rotor (for example, the first rotor 13 or the second rotor 14) in the rotor assembly 10 at intervals of a preset time (for example, 1 second), and the rotation speed information can be detected by the detection assembly 222. It can be understood that, in order to cope with the abnormal power failure situation, the power source adopted by the detection component 222 and the first magnetic member 21 is a standby power source.

The rotation speed change rate refers to a change of a rotation speed of one rotor in the rotor assembly 10, so as to determine whether the rotation speed is reduced or not and further determine whether the machine is turned off, where the rotation speed information includes a first rotation speed and a second rotation speed of the rotor assembly 10 at a preset time interval, and the rotation speed change rate of the rotor assembly 10 calculated according to the rotation speed information may be calculated according to the first rotation speed, the second rotation speed and the preset time, for example, as shown in the following formula:

P＝(n1-n2)/T；

wherein n1 is a first rotation speed, n2 is a second rotation speed, and T is a preset time.

The preset rotation speed change rate is a rotation speed change rate limit value built in the compressor control software/program, for example, the preset rotation speed change rate may be-10 r/min × min, that is, when the rotation speed change rate is less than 0, it may be determined that the compressor is abnormally shut down, and at this time, the protection mechanism is triggered to open the first magnetic member 21, so as to ensure that the axial force F of the compressor is balanced under the abnormal shut-down condition.

To facilitate closing the first magnetic member 21 after the rotor assembly 10 stops rotating, in some embodiments of the present application, referring to fig. 8, fig. 8 shows a schematic flow chart of closing the first magnetic member 21 in embodiments of the present application, wherein after the compressor is turned off to stop providing power to the rotor assembly 10, the method further comprises:

step S801, acquiring a rotation speed of the rotor assembly 10;

in step S802, when the rotation speed is less than or equal to the preset rotation speed, the first magnetic member 21 is turned off.

The preset rotation speed is a rotation speed limit value built in the compressor control software/program, for example, the preset rotation speed may be 10r/min, and when the rotation speed is less than or equal to the preset rotation speed, the rotor assembly 10 is already close to the stop state, so the first magnetic member 21 may be turned off to save power.

Further, in order to facilitate the control of the magnitude of the first magnetic force F1 and avoid the phenomenon that the first magnetic force F1 is too large to cause the overload of the axial force limiter 30, referring to fig. 9, fig. 9 shows a schematic flow chart of the control of the initial input power of the first magnetic member 21 in the embodiment of the present application, wherein the step of turning on the first magnetic member 21 comprises:

step S901, acquiring a rotation speed of the rotor assembly 10;

in step S902, the input power to the first magnetic member 21 is determined according to the rotation speed of the rotor assembly 10, so as to control the magnitude of the first magnetic force F1.

Since the rotation speed of the rotor assembly 10 is proportional to the axial force F, the input power to the first magnetic member 21 can be determined according to the rotation speed of the rotor assembly 10 to control the magnitude of the first magnetic force F1, thereby avoiding the phenomenon that the axial force limiter 30 is overloaded due to the overlarge first magnetic force F1.

Further, in order to avoid the phenomenon that the axial force F is reduced and the first magnetic force F1 is too large to cause the overload of the axial force limiter 30 after the step of turning on the first magnetic element 21 is performed, referring to fig. 10, fig. 10 shows a schematic flow chart of controlling the input power of the first magnetic element 21 in the embodiment of the present application, wherein after the step of turning on the first magnetic element 21, the method for turning off the motor further includes:

step S1001, obtaining rotational speed information of the rotor assembly 10;

step S1002, calculating a rotation speed change rate of the rotor assembly 10 according to the rotation speed information;

in step S1003, the rate of change of the input power of the first magnetic member 21 is determined according to the rate of change of the rotation speed, so as to reduce the first magnetic force F1 as the rotation speed of the rotor assembly 10 decreases during the shutdown of the compressor.

The rotation speed information includes a first rotation speed and a second rotation speed of the rotor assembly 10 at intervals of a preset time, and the rotation speed change rate of the rotor assembly 10 calculated according to the rotation speed information may be calculated according to the first rotation speed, the second rotation speed and the preset time. Since the rotation speed of the rotor assembly 10 is proportional to the axial force F, the change rate of the input power to the first magnetic member 21 can be determined according to the change rate of the rotation speed of the rotor assembly 10, and the first magnetic force F1 is synchronously reduced to control the magnitude of the first magnetic force F1, thereby avoiding the phenomenon that the axial force limiting member 30 is overloaded due to the overlarge first magnetic force F1.

It should be noted that the above description of the compressor shutdown method is only for the purpose of clearly illustrating the verification process of the present invention, and those skilled in the art can make equivalent modifications to the above method under the guidance of the present invention, for example, the controller can also issue a command to open the first magnetic member 21 5 seconds in advance and then close the compressor.

Further, in order to better implement the compressor in the present application, on the basis of the compressor, an embodiment of the present invention further provides an air conditioner, where the air conditioner includes the compressor in any one of the above embodiments, and the air conditioner in the embodiment of the present application has all beneficial effects of the compressor due to the arrangement of the compressor in the above embodiment, and therefore, details are not described here again.

In the above embodiments, the descriptions of the respective embodiments have respective emphasis, and parts that are not described in detail in a certain embodiment may refer to the above detailed descriptions of other embodiments, and are not described herein again.

Having thus described the basic concept, it will be apparent to those skilled in the art that the foregoing detailed disclosure is to be considered merely illustrative and not restrictive of the broad application. Various modifications, improvements and adaptations to the present application may occur to those skilled in the art, although not explicitly described herein. Such modifications, improvements and adaptations are proposed in the present application and thus fall within the spirit and scope of the exemplary embodiments of the present application.

Also, this application uses specific language to describe embodiments of the application. Reference throughout this specification to "one embodiment," "an embodiment," and/or "some embodiments" means that a particular feature, structure, or characteristic described in connection with at least one embodiment of the present application is included in at least one embodiment of the present application. Therefore, it is emphasized and should be appreciated that two or more references to "an embodiment" or "one embodiment" or "an alternative embodiment" in various places throughout this specification are not necessarily all referring to the same embodiment. Furthermore, some features, structures, or characteristics of one or more embodiments of the present application may be combined as appropriate.

Similarly, it should be noted that in the preceding description of embodiments of the application, various features are sometimes grouped together in a single embodiment, figure, or description thereof for the purpose of streamlining the disclosure aiding in the understanding of one or more of the embodiments. This method of disclosure, however, is not intended to require more features than are expressly recited in the claims. Indeed, the embodiments may be characterized as having less than all of the features of a single embodiment disclosed above.

Numerals describing the number of components, attributes, etc. are used in some embodiments, it being understood that such numerals used in the description of the embodiments are modified in some instances by the use of the modifier "about", "approximately" or "substantially". Unless otherwise indicated, "about", "approximately" or "substantially" indicates that the number allows a variation of ± 20%. Accordingly, in some embodiments, the numerical parameters used in the specification and claims are approximations that may vary depending upon the desired properties of the individual embodiments. In some embodiments, the numerical parameter should take into account the specified significant digits and employ a general digit preserving approach. Notwithstanding that the numerical ranges and parameters setting forth the broad scope of the range are approximations, in the specific examples, such numerical values are set forth as precisely as possible within the scope of the application.

For each patent, patent application publication, and other material cited in this application, such as articles, books, specifications, publications, documents, and the like, the entire contents of which are hereby incorporated by reference into this application, except for application history documents that are inconsistent with or conflict with the contents of this application, and except for documents that are currently or later become incorporated into this application as though fully set forth in the claims below. It is noted that the descriptions, definitions and/or use of terms in this application shall control if they are inconsistent or contrary to the present disclosure.

The compressor, the shutdown method thereof, and the air conditioner provided in the embodiments of the present application are described in detail above, and specific examples are applied herein to explain the principles and embodiments of the present invention, and the description of the embodiments above is only used to help understand the method and the core idea of the present invention; 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 compressor, comprising:

a rotor assembly including a first rotating shaft and a first rotor having a first working portion and a second working portion coaxially connected to the first rotating shaft and having opposite thread directions, the first working portion and the second working portion being rotatable along a first axis, the first working portion and the second working portion generating an axial force in a direction of the first axis when rotated along the first axis;

the magnetic assembly comprises a first magnetic part, and the first magnetic part is used for generating a first magnetic force along the first axial direction before the compressor is shut down, so that the resultant force of the first magnetic force and the axial force is towards a preset direction or is 0 along the first axial direction in the shutdown process of the compressor.

2. The compressor of claim 1, wherein the magnetic assembly further comprises a second magnetic member for generating a second magnetic force in the same direction as the first magnetic force when the compressor is in an operating state.

3. The compressor of claim 2, wherein the first magnetic member and the second magnetic member are located at the same end of the first shaft; or

4. The compressor of claim 2, wherein the second magnetic member includes a driving motor coupled to the first rotating shaft, the driving motor for generating a second magnetic force in the same direction as the first magnetic force.

5. The compressor of claim 4, wherein the drive motor includes a motor stator and a motor rotor spaced apart from each other, the motor rotor being coupled to the first shaft;

the motor stator comprises a first end face, the motor rotor comprises a second end face located on the same side as the first end face, and the first end face and the second end face are arranged in a staggered mode in the axial direction of the first rotating shaft.

6. The compressor of claim 5, wherein the distance between the first end surface and the rotor assembly is greater than the distance between the second end surface and the rotor assembly, and the second magnetic member is disposed at the same end of the first rotating shaft as the first magnetic member; or

7. The compressor of claim 5 wherein said first magnetic member is located at an end of said first shaft proximate said drive motor, said drive motor further comprising a shield surrounding said motor stator and said motor rotor.

8. The compressor of claim 1, further comprising a sensing assembly for sensing a rotation speed of the first rotating shaft to turn on, turn off, or control an input power of the first magnetic member according to the rotation speed of the first rotating shaft.

9. The compressor of claim 1 or 2, further comprising an axial force limiter disposed at one end of the first rotating shaft, the axial force limiter being configured to generate an axial thrust force that cancels out a resultant force of the first magnetic force or the second magnetic force and the axial force.

10. The compressor of claim 1 wherein said rotor assembly further comprises a second rotor having a first sub-working portion in meshing engagement with said first working portion and a second sub-working portion in meshing engagement with said second working portion.

11. A compressor shutdown method applied to the compressor according to any one of claims 1 to 10, comprising:

the method comprises the steps that a first magnetic piece is started before the compressor is shut down, and the first magnetic piece generates first magnetic force along a first axial direction;

and closing the compressor to stop providing power for the rotor assembly, wherein the resultant force of the axial force generated by rotation of the rotor assembly in the shutdown process and the first magnetic force is towards a preset direction or is 0 along the first axis.

12. The method for shutting down a compressor of claim 11, wherein prior to the step of turning on said first magnetic member, said method further comprises:

acquiring rotating speed information of the rotor assembly;

and when the rotating speed change rate is smaller than or equal to a preset rotating speed change rate, starting the first magnetic piece.

13. The method of compressor shutdown as recited in claim 11, wherein after said shutting down the compressor to stop providing power to the rotor assembly, the method further comprises:

acquiring the rotating speed of the rotor assembly;

and when the rotating speed is less than or equal to a preset rotating speed, closing the first magnetic piece.

14. The compressor shutdown method as claimed in claim 11, wherein said step of turning on said first magnetic member includes:

acquiring the rotating speed of the rotor assembly;

and determining the input power to the first magnetic part according to the rotating speed of the rotor assembly so as to control the magnitude of the first magnetic force.

15. The method for shutting down a compressor of claim 11, wherein after the step of turning on the first magnetic member, the method further comprises:

acquiring rotating speed information of the rotor assembly;

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