CN113027789A

CN113027789A - Gas suspension compressor and refrigeration equipment

Info

Publication number: CN113027789A
Application number: CN202110424138.4A
Authority: CN
Inventors: 刘华; 张治平; 杨玉明; 陈玉辉; 周宇
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2020-04-20
Filing date: 2021-04-20
Publication date: 2021-06-25
Also published as: CN214617124U; CN111396336A

Abstract

The invention relates to a gas suspension compressor and refrigeration equipment. Wherein, gas suspension compressor includes: a housing; the rotor is rotatably arranged in the shell; the first impeller is arranged at the first axial end of the rotor; the second impeller is arranged at the second axial end of the rotor; the first adjusting ring is arranged at the first axial end of the rotor and forms a first gap with the first impeller, the first gap is positioned in the first gas compression area, and the first adjusting ring is configured to counteract partial axial force generated by gas pressure difference between the first gas compression area and the first gap; and the second adjusting ring is arranged at the second axial end of the rotor, and forms a second gap with the second impeller, the second gap is positioned in the second gas compression area, and the second adjusting ring is configured to counteract partial axial force generated by the gas pressure difference between the second gas compression area and the second gap. The invention can reduce axial force to a great extent and improve the operation reliability of the gas suspension compressor by the back-to-back impeller and the double adjusting rings.

Description

Gas suspension compressor and refrigeration equipment

Technical Field

The invention relates to the field of electrical equipment, in particular to a gas suspension compressor and refrigeration equipment.

Background

The air suspension compressor is a compressor which utilizes a gas bearing to support a rotor and has the characteristics of large limit rotating speed, strong self-adaptive stability and the like. However, in the process of compressing gas by the impeller of the gas suspension compressor, the rotor of the motor may move, which affects the usability of the gas suspension compressor. In the related art, an axial gas bearing is generally used to prevent the rotor from moving, however, the larger the moving amplitude of the rotor of the motor is, the higher the possibility of failure of the axial gas bearing is, and the worse the operation reliability of the air suspension compressor is.

Disclosure of Invention

Some embodiments of the invention provide a gas suspension compressor and a refrigeration device, which are used for relieving the problem of large rotor movement amplitude.

Some embodiments of the present invention provide a gas suspension compressor, comprising:

a housing;

the rotor is rotatably arranged in the shell;

a first impeller disposed at a first axial end of the rotor, the first impeller configured to rotate to form a first pre-gas compression zone forward of the first impeller and a first post-gas compression zone rearward of the first impeller;

a second impeller provided at a second axial end of the rotor, the second impeller configured to rotate to form a second pre-gas-compression region in front of the second impeller and a second post-gas-compression region behind the second impeller;

a first adjusting ring disposed at a first axial end of the rotor, the first adjusting ring forming a first gap with the first impeller, the first gap being located in the first gas post-compression region, the first adjusting ring being configured to counteract a portion of an axial force generated by a gas pressure differential within the first gas pre-compression region and the first gap; and

a second adjustment ring disposed at a second axial end of the rotor, a second gap being formed between the second adjustment ring and the second impeller, the second gap being located in the second post-gas-compression region, the second adjustment ring being configured to counteract a portion of an axial force generated by a gas pressure differential between the second pre-gas-compression region and the second gap.

In some embodiments, a motor cavity is formed within the housing;

the gas pressure within the motor cavity acts on the first adjustment ring, the first adjustment ring configured to counteract a portion of an axial force generated by the first pre-gas compression region, the first gap, and a gas pressure differential within the motor cavity, and/or,

the gas pressure within the motor cavity acts on the second adjustment ring, which is configured to counteract a portion of the axial force generated by the second gas pre-compression region, the second gap, and the gas pressure differential within the motor cavity.

In some embodiments, the first adjusting ring has an outer diameter less than or equal to an outer diameter of the first impeller, and/or the second adjusting ring has an outer diameter less than or equal to an outer diameter of the second impeller.

In some embodiments, the gas suspension compressor further comprises:

the outer periphery of the first diffuser is connected to the inner wall of the shell, the first comb tooth sealing structure is arranged between the inner periphery of the first diffuser and the first adjusting ring, and/or,

annular second diffuser and second broach seal structure, the periphery of second diffuser connect in the inner wall of casing, second broach seal structure locate the inner periphery of second diffuser with between the second adjustable ring.

In some embodiments, the air suspension compressor further includes an axial bearing assembly located at the first axial end of the rotor and proximate an axially middle portion of the housing relative to the first adjustment ring.

In some embodiments, an inner diameter of the axial bearing assembly is the same as an inner diameter of the first adjustment ring, and an outer diameter of the axial bearing assembly is greater than an outer diameter of the first adjustment ring.

In some embodiments, the axial bearing assembly comprises:

the thrust disc is arranged on the rotor;

a first axial bearing located between the thrust disc and the first adjustment ring; and

and the second axial bearing is positioned on one side of the thrust disc, which is far away from the first axial bearing.

In some embodiments, the air suspension compressor further comprises a first radial bearing located at the first axial end of the rotor and proximate an axial middle of the housing relative to the axial bearing assembly.

In some embodiments, the gas suspension compressor further comprises:

a first diffuser having an outer circumference connected to an inner wall of the housing, the first adjusting ring being located between the inner circumference of the first diffuser and the rotor; and

the first bearing seat is connected to the inner wall of the shell, and the first radial bearing is arranged on the first bearing seat;

wherein the axial bearing assembly is located between the first diffuser and the first bearing seat.

In some embodiments, the axial bearing assembly includes a thrust disk, a first axial bearing, and a second axial bearing; the thrust disc is arranged on the rotor; the first axial bearing is located between the thrust disc and the first adjusting ring and is connected to the first diffuser; the second axial bearing is located between the thrust disk and the first bearing seat and connected to the first bearing seat.

In some embodiments, a third gap is formed between the first diffuser and the first bearing seat near the rotor, the axial bearing assembly is located in the third gap, and the first diffuser and the first bearing seat are attached to each other at a position far away from the rotor.

In some embodiments, the rotor includes a first shaft segment and a second shaft segment, the first shaft segment having a diameter smaller than a diameter of the second shaft segment, the first adjustment ring and the axial bearing assembly located at the first shaft segment, the first radial bearing located at the second shaft segment.

In some embodiments, the air suspension compressor further comprises a second radial bearing located at a second axial end of the rotor and proximate an axial middle of the housing relative to the second adjustment ring.

In some embodiments, the gas suspension compressor further comprises:

a second diffuser having an outer circumference connected to an inner wall of the housing, the second diffuser having the second adjusting ring between an inner circumference of the second diffuser and the rotor; and

the second bearing seat is connected to the inner wall of the shell, and the second radial bearing is arranged on the second bearing seat; the second bearing seat is attached to the second diffuser.

In some embodiments, the rotor has shaft sections of different diameters, the diameter of the shaft section of the rotor at which the second adjusting ring is located being smaller than the diameter of the shaft section of the rotor at which the second radial bearing is located.

In some embodiments, the gas suspension compressor further comprises:

a first volute disposed at a first axial end of the housing and surrounding the first impeller, the first gas pre-compression region and the first gas post-compression region being located within the first volute and being in communication with each other; and/or the presence of a gas in the gas,

and the second volute is arranged at the second axial end of the shell and surrounds the second impeller, and the second gas before-compression area and the second gas after-compression area are positioned in the second volute and are communicated with each other.

In some embodiments of the present invention, the,

the material hardness of the first adjusting ring is greater than the material hardness of the first diffuser; and/or the presence of a gas in the gas,

the material hardness of the second adjusting ring is greater than the material hardness of the second diffuser.

In some embodiments of the present invention, the,

the difference between the material hardness of the first adjusting ring and the material hardness of the first diffuser is more than or equal to 15 HRC; and/or the presence of a gas in the gas,

the difference between the material hardness of the second adjusting ring and the material hardness of the second diffuser is larger than or equal to 15 HRC.

In some embodiments, the axial dimension of the first gap is ≧ 0.6mm, and/or the axial dimension of the second gap is ≧ 0.6 mm.

Some embodiments provide a gas suspension compressor, comprising:

a compressor body having a gas pre-compression region and a gas post-compression region in communication within the compressor body, the compressor body including a rotor and an impeller; and

an adjusting ring sleeved on the rotor, wherein the adjusting ring is positioned in the gas compression area and has an adjusting gap with the impeller so as to offset partial axial force generated by gas pressure difference between the gas compression area and the gas compression area;

wherein the axial size of the adjusting clearance is more than or equal to 0.6 mm.

Some embodiments provide a gas suspension compressor, comprising:

the compressor comprises a compressor main body, a compressor main body and a compressor control unit, wherein the compressor main body is internally provided with a gas compression front area and a gas compression rear area which are communicated with each other, and comprises a rotor, an impeller and a diffuser; and

the comb tooth sealing structure is arranged between the adjusting ring and the diffuser, and the material hardness of the adjusting ring is larger than that of the diffuser.

In some embodiments, the difference between the material hardness of the adjusting ring and the material hardness of the diffuser is greater than or equal to 15 HRC.

Some embodiments provide a gas suspension compressor, comprising:

wherein the axial size of the adjusting gap is more than or equal to 0.6 mm;

the adjustable ring is characterized in that a comb tooth sealing structure is arranged between the adjustable ring and the diffuser, and the material hardness of the adjustable ring is greater than that of the diffuser.

Some embodiments provide an air suspension compressor comprising: a compressor body and an adjustment ring;

the compressor body is internally provided with a gas compression front area and a gas compression rear area which are communicated;

the adjusting ring is sleeved on a rotor of a motor of the compressor main body, is positioned in the gas compression region and has an adjusting gap with an impeller of the compressor main body, so that partial axial force generated by gas pressure difference between the gas compression region and the gas compression region is offset.

In some embodiments, the adjusting ring is fixed to the rotor of the electric machine by interference fit.

In some of these embodiments, the compressor body comprises: the centrifugal pump comprises a shell, a first diffuser arranged at a first opening of the shell, a first volute covering the shell, a first impeller positioned in the first volute, and a motor, a first radial bearing and an axial bearing assembly which are arranged in the shell;

a first axial end of a rotor of the motor sequentially penetrates through the first radial bearing, the axial bearing assembly and the first diffuser to be connected with the first impeller;

the adjusting ring comprises a first adjusting ring which is positioned in the first diffuser and forms the adjusting gap with the first impeller, and the adjusting gap is a first gap.

In some of these embodiments, the first radial bearing is secured within the housing by a first bearing seat.

In some of these embodiments, a first step surface is provided within the housing;

the first bearing seat is abutted between the first diffuser and the first step surface.

In some embodiments, a second step surface is arranged on the outer wall of the rotor;

an inner ring portion of the axial bearing assembly is limited in a containing cavity formed between the first adjusting ring and the second step surface, and an outer ring portion of the axial bearing assembly is connected between the first diffuser and the first bearing seat.

In some embodiments, a third step surface is arranged at the first opening of the housing, and a fourth step surface is arranged on the outer wall of the first diffuser;

the fourth step surface is overlapped on the third step surface through a fastener.

In some of these embodiments, the compressor body further comprises: the second diffuser is arranged at a second opening of the shell, the second volute is covered on the shell, the second impeller is positioned in the second volute, and the second radial bearing is arranged in the shell;

and the second axial end of the rotor sequentially penetrates through the second radial bearing and the second diffuser to be connected with the second impeller.

In some of these embodiments, the tuning ring further includes a second tuning ring located within the second diffuser and forming the tuning gap with the second impeller, where the tuning gap is a second gap.

In some of these embodiments, the second radial bearing is secured within the housing by a second bearing housing.

In some embodiments, a fifth step surface is provided in the housing;

the second bearing seat is abutted between the second diffuser and the fifth step surface.

In some embodiments, a sixth step surface is arranged at the second opening of the housing, and a seventh step surface is arranged on the outer wall of the second diffuser;

the seventh step surface is overlapped on the sixth step surface through a fastener.

In some embodiments, an eighth step surface is arranged on the outer wall of the rotor;

the second adjusting ring is abutted to the eighth step surface.

Some embodiments also provide a refrigeration apparatus comprising the above-described gas suspension compressor.

Based on the technical scheme, the invention at least has the following beneficial effects:

in some embodiments, the first impeller and the second impeller are arranged back to back and are respectively arranged at two axial ends of the rotor, the axial forces are mutually offset by utilizing a method that the gas pressure borne by the first impeller is opposite to that borne by the second impeller, and finally, the axial forces are weakened, so that the accumulation of the axial forces of the gas suspension compressor is avoided; because the back of the impeller can be subjected to pressure caused by air pressure, the adjusting ring is fixed on the rotor, and the stress area of the back of the impeller can be adjusted through the adjusting ring so as to reduce the stress area of the impeller and further reduce the axial force; through back of the body impeller structure + two regulation ring structures, but to a great extent reduces the axial force, improves bearing air film thickness and bearing factor of safety.

In some embodiments, in the above air suspension compressor and the refrigeration apparatus, the adjusting ring is sleeved on the rotor of the motor, the adjusting ring is located in the region after the air compression and has an adjusting gap with the impeller, when the rotor of the motor drives the adjusting ring and the impeller to rotate, the air in the adjusting gap generates a pressure on the adjusting ring, the pressure is opposite to and the same as the direction and the magnitude of the axial force borne by the portion of the back surface of the impeller, which is opposite to the adjusting ring, so that a partial axial force generated by the air pressure difference between the region after the air compression and the region before the air compression can be counteracted, and it is ensured that an air film formed in the axial bearing assembly has a certain thickness, thereby reducing the failure probability of the axial bearing assembly, and improving the operation reliability of the air.

Drawings

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without limiting the invention. In the drawings:

FIG. 1 is a schematic diagram of a gas suspension compressor provided in accordance with some embodiments of the present invention;

FIG. 2 is an enlarged partial schematic view of FIG. 1 at I;

FIG. 3 is an enlarged partial schematic view at III of FIG. 2;

fig. 4 is a partially enlarged schematic view at II of fig. 1.

The reference numbers in the drawings illustrate the following:

a1 — first gas pre-compression zone; b1 — first gas post-compression zone;

a2 — second gas pre-compression zone; b2 — second gas post-compression zone;

110-a motor; 111-a rotor; 112-a stator;

120 a-a first impeller; 120 b-a second impeller;

130-a housing; 131-a motor cavity;

140 a-a first diffuser; 140 b-a second diffuser;

150 a-a first volute; 151 a-first inlet port; 152 a-a first air outlet;

150 b-a second volute; 151 b-second inlet port; 152 b-a second outlet port;

160 a-first radial bearing; 160 b-a second radial bearing;

170-axial bearing assembly; 171-a first axial bearing; 172-a thrust disk; 173-second axial bearing;

180 a-a first bearing seat; 180 b-a second bearing housing;

190 a-a first gap; 190 b-a second gap;

200 a-a first adjusting ring; 200 b-a second adjusting ring;

210 a-a first comb structure; 210 b-second comb tooth structure.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments. It is to be understood that the described embodiments are merely a few embodiments of the invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments of the present invention without any inventive step, are within the scope of the present invention.

In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are not to be considered limiting of the 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, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like as used herein are for illustrative purposes only and do not denote a unique embodiment.

Referring to fig. 1, fig. 1 illustrates a schematic structural view of an air suspension compressor according to some embodiments of the present invention, and some embodiments of the present invention provide an air suspension compressor including: a compressor body and an adjustment ring; the compressor body is internally provided with gas pre-compression areas A1 and A2 and gas post-compression areas B1 and B2 which are communicated; the adjusting ring is sleeved on the rotor 111 of the motor 110 of the compressor body, is positioned in the gas compression rear areas B1 and B2 and has an adjusting gap with the impeller of the compressor body so as to offset part of the axial force generated by the gas pressure difference between the gas compression rear areas B1 and B2 and the gas compression front areas A1 and A2.

It should be noted that, in the process of compressing gas by the impeller of the gas suspension compressor, there is a pressure difference between before and after the refrigerant gas is compressed, and the rotor 111 of the motor 110 is axially moved by an axial force from after the gas is compressed to before the gas is compressed. While the axial force is usually counteracted by using an axial gas bearing in the related art, the axial gas bearing comprises a thrust bearing and a thrust disk which are sequentially distributed at intervals along the axial direction of the rotor 111 of the motor 110, and the principle of counteracting the axial force is as follows: the rotor 111 of the motor 110 is rotated at a high speed to drive the thrust plate to rotate, and after the thrust plate reaches a certain rotating speed, an air film is formed between the thrust plate and the surface of the thrust bearing, and the air film has a certain bearing capacity and can support the axial force. However, the thickness of the gas film is inversely proportional to the magnitude of the axial force borne by the rotor 111 of the motor 110, that is, the greater the axial force borne by the rotor 111 of the motor 110, the smaller the gas film thickness, and the greater the possibility of the axial gas bearing failing.

After gas compression, the gas pressure of the regions B1 and B2 is greater than that of the regions a1 and a2 before gas compression, and the direction of the axial force generated by the gas pressure difference between the regions B1 and B2 after gas compression and the regions a1 and a2 before gas compression is directed to the regions a1 and a2 before gas compression by the regions B1 and B2 after gas compression.

For example: the back of the impeller is subjected to an axial force F1 (see fig. 2). Further, the adjusting gap between the adjusting ring and the impeller is used as a part of the area B1 after the gas is compressed, and when the rotor 111 of the motor 110 drives the adjusting ring and the impeller to rotate, the gas in the adjusting gap generates a pressure Fx on the adjusting ring₁(see FIG. 2), the Fx₁The axial force F1 received by the portion of the back face of the impeller opposite the adjusting ring is opposite in direction and equal in magnitude, so that the force Fx₁The partial axial force born by the back of the impeller is counteracted, and the stress area of the back of the impeller is reduced, namely the pressure area of the axial force F1 to the impeller is equal to that of the impeller

Wherein R is_ImpellerIs the outer radius of the impeller, R_{Adjusting ring}To adjust the ring outer radius, part of the axial force between the post-gas compression zone B1 and the pre-gas compression zone a1 due to the gas pressure differential is cancelled out. In addition, the arrows in fig. 1 represent the gas flow direction.

As above, the rotor 111 of the motor 110 is sleeved with the adjusting ring, the adjusting ring is located in the gas compression regions B1 and B2 and has an adjusting gap with the impeller, when the rotor 111 of the motor 110 drives the adjusting ring and the impeller to rotate, the gas in the adjusting gap generates a pressure to the adjusting ring, the pressure is opposite to and the same as the direction and the magnitude of the axial force borne by the portion of the back surface of the impeller, which is opposite to the adjusting ring, which can counteract the partial axial force generated by the gas pressure difference between the gas compression regions B1 and B2 and the gas compression regions a1 and a2, so as to ensure that the gas film formed by the axial bearing assembly 170 has a certain thickness, thereby reducing the failure probability of the axial bearing assembly 170, and improving the operation reliability of the gas suspension compressor.

With regard to the setting of the size of the adjusting ring, it can be seen from the above description that the force-bearing area of the axial force F1 on the impeller is equal to that of the impeller

The larger the outer diameter of the adjusting ring, the smaller the force area of the axial force F1 on the impeller, and the smaller the axial force F1.

Because the pressure in the cavity of the motor 110 is small, the compressed gas can generate a pressure difference with the gas in the cavity of the motor 110, and further a pressure Fx can be generated on the adjusting ring₃(see FIG. 3), the force direction is directed to the motor cavity, the pressure Fx₃The force-bearing area of the adjusting ring being the adjusting ring area of the adjusting ring, i.e.

Wherein r is_{Adjusting ring}For adjusting the inner radius of the ring, the smaller the outer diameter of the adjusting ring, the smaller the force-bearing area, Fx₃The smaller. From the above, the adjusting ring size affects F1, Fx₃The size of the adjusting ring is selected, and comprehensive evaluation and selection are required according to compressors with different power and different working conditions.

In some embodiments of the present invention, the adjusting ring is fixed to the rotor 111 of the motor 110 by interference fit. Thus, the adjusting ring can be firmly sleeved on the rotor 111 of the motor 110 to effectively rotate along with the rotor 111 of the motor 110.

It should be noted that the inner diameter of the adjusting ring is smaller than the outer diameter of the rotor 111, so as to achieve a tight coupling between the adjusting ring and the rotor 111 by means of an interference fit.

In some embodiments of the invention, the adjusting ring has an outer diameter that is less than or equal to the outer diameter of the impeller.

In some embodiments of the invention, the axial dimension of the adjustment clearance is ≧ 0.6 mm.

In some embodiments of the present invention, an air suspension compressor includes a compressor body and an adjustment ring.

The compressor body has a gas pre-compression region and a gas post-compression region in communication with each other, and includes a rotor 111, an impeller, and a diffuser.

The adjusting ring is sleeved on the rotor 111, is located in the gas compression area and has an adjusting gap with the impeller so as to offset part of axial force generated by gas pressure difference between the gas compression area and the gas compression area.

In some embodiments of the present invention, a comb seal structure is disposed between the adjusting ring and the diffuser, and the material hardness of the adjusting ring is greater than that of the diffuser.

Optionally, the difference between the hardness of the material of the adjusting ring and the hardness of the material of the diffuser is greater than or equal to 15 HRC.

In some embodiments of the present invention, as shown in fig. 1, the compressor body includes: a housing 130, a first diffuser 140a disposed at a first opening of the housing 130, a first volute 150a covering the first opening of the housing 130, a first impeller 120a disposed in the first volute 150a, and a motor 110, a first radial bearing 160a, and an axial bearing assembly 170 disposed in the housing 130; a first axial end of the rotor 111 of the motor 110 sequentially passes through the first radial bearing 160a, the axial bearing assembly 170 and the first diffuser 140a, and is connected with the first impeller 120 a; the regulation ring includes a first regulation ring 200a, and the first regulation ring 200a is located between the inner circumference of the first diffuser 140a and the rotor 111, and forms a first gap 190a with the first impeller 120 a. It will be appreciated that there is a slight gap between the first tuning ring 200a and the first diffuser 140a and between the first tuning ring 200a and the axial bearing assembly 170, the width of which is determined primarily by the type of compressor.

Optionally, the axial dimension of the first gap 190a is ≧ 0.6 mm.

It should be noted that, as shown in fig. 1, the first volute 150a has a first inlet 151a and a first outlet 152 a. When the first impeller 120a rotates at a high speed, the gas enters the first volute 150a from the first gas inlet 151a, and the first impeller 120a compresses the gas in cooperation with the first diffuser 140a and discharges the gas through the first gas outlet 152 a.

Alternatively, as shown in fig. 1, the housing 130 is an irregular cylindrical structure, and may be formed by casting, and mainly plays a role in supporting, protecting and absorbing shock.

Alternatively, as shown in fig. 1, the motor 110 includes: a rotor 111 and a stator 112, the stator 112 being constituted by a winding to provide a magnetic field to the rotor 111; the rotor 111 can be rotated at high speed in the magnetic field. The stator 112 may be fixed in the housing 130 by screws or interference fit.

In some embodiments of the present invention, a first comb seal arrangement 210a is mounted between the first diffuser 140a and the first tuning ring 200 a. Wherein the first comb tooth sealing structure 210a is installed on the first diffuser 140 a.

In some embodiments of the present invention, the material hardness of the first tuning ring 200a is greater than the material hardness of the first diffuser 140 a.

Optionally, the difference between the material hardness of the first tuning ring 200a and the material hardness of the first diffuser 140a is greater than or equal to 15 HRC.

Optionally, the first radial bearing 160a is a gas bearing. The bearing is a sliding bearing using a gas as a lubricant, and the most commonly used gas lubricant is air, and if necessary, a gas such as nitrogen, argon, hydrogen, helium, or carbon dioxide may be used. It should be noted that the first radial bearing 160a limits the position of the rotor 111 in the radial direction of the rotor 111, and the axial bearing assembly 170 limits the position of the rotor 111 in the axial direction of the rotor 111 (i.e., the left-right direction shown in fig. 1).

Further, in some embodiments of the present invention, as shown in FIG. 1, the first radial bearing 160a is secured within the housing 130 by a first bearing seat 180 a.

In some embodiments of the present invention, as shown in fig. 1, a first step surface is disposed on an inner wall of the housing 130; the first bearing seat 180a abuts between the first diffuser 140a and the first step surface. Thus, the first bearing seat 180a is convenient to disassemble and assemble.

Optionally, as shown in fig. 1, a ninth step surface is disposed on an outer wall of the first bearing seat 180a, and a limiting protrusion is disposed on the first diffuser 140 a; the limiting bulge is abutted against the ninth step surface. Therefore, the installation firmness of the first bearing seat 180a in the housing 130 can be increased, and the first bearing seat 180a is prevented from shaking.

In some embodiments of the present invention, as shown in fig. 1, a second step surface is disposed on an outer wall of the rotor 111; the inner race portion of the axial bearing assembly 170 is confined in the receiving cavity formed between the first adjusting ring 200a and the second step surface, and the outer race portion of the axial bearing assembly 170 is connected between the first diffuser 140a and the first bearing housing 180 a. Note that, as shown in fig. 2, the axial bearing assembly 170 includes: a first axial bearing 171 fixed on the first diffuser 140a, a thrust disk 172 sleeved on the rotor 111 of the motor 110, and a second axial bearing 173 fixed on the first bearing seat 180 a. Thus, when the rotor 111 of the motor 110 is subjected to an axial force, a stable dynamic air film is formed between the thrust disk 172 of the axial bearing assembly 170 and the first axial bearing 171, which can effectively support the axial force applied to the rotor 111 of the motor 110.

In some embodiments of the present invention, as shown in fig. 1, a third step surface is disposed at the first opening of the housing 130, and a fourth step surface is disposed on an outer wall of the first diffuser 140 a; the fourth step surface is overlapped on the third step surface through a fastener. According to the fixing manner of the first diffuser 140a, the first diffuser 140a and the first opening of the housing 130 can be kept flush, so that excessive parts of the first diffuser 140a are prevented from extending into the first volute 150a, and the compressed gas is ensured to smoothly flow out from the first gas outlet 152a of the first volute 150 a.

As shown in fig. 1, in some embodiments of the invention, the compressor body further comprises: a second diffuser 140b disposed at the second opening of the housing 130, a second volute 150b covering the second opening of the housing 130, a second impeller 120b disposed in the second volute 150b, and a second radial bearing 160b disposed in the housing 130; the second axial end of the rotor 111 of the motor 110 passes through the second radial bearing 160b and the second diffuser 140b in this order, and is connected to the second impeller 120 b. In the process that the rotor 111 of the motor 110 drives the impeller to rotate, the impeller generates an axial force due to the structure of the impeller, and therefore, the first impeller 120a and the second impeller 120b are arranged on two sides of the rotor 111, the principle that the gas pressure borne by the first impeller 120a is opposite to that borne by the second impeller 120b can be utilized, so that partial axial forces are mutually offset, and finally, the axial force is weakened, and the problem that the axial force is accumulated due to the fact that the first impeller 120a and the second impeller 120b are arranged on the same side of the rotor 111 in a conventional gas suspension compressor is solved.

In some embodiments of the present invention, a second comb seal arrangement 210b is mounted between the second diffuser 140b and the second tuning ring 200 b. Wherein the second comb seal structure 210b is mounted on the second diffuser 140 b.

In some embodiments of the present invention, the material hardness of the second tuning ring 200b is greater than the material hardness of the second diffuser 140 b.

Optionally, the difference between the material hardness of the second adjusting ring 200b and the material hardness of the second diffuser 140b is greater than or equal to 15 HRC.

Further, as shown in fig. 1, in some embodiments of the present invention, the regulation ring further includes a second regulation ring 200b, the second regulation ring 200b being located between an inner periphery of the second diffuser 140b and the rotor 111, and forming a second gap 190b with the second impeller 120 b. The rotor 111 of the motor 110 drives the second impeller 120b to perform high-speed rotation, and the second diffuser 140b cooperates with the second impeller 120b to perform secondary compression on the gas sucked into the second scroll 150 b. Similar to the first impeller 120a, the pressure at the back of the second impeller 120b is greater than the pressure at the second inlet 151b, resulting in an axial force F2 (shown as F2)4) to push the second impeller 120b toward the second inlet 151 b. Gas within a second gap 190b between the second adjustment ring 200b and the second impeller 120b may generate a pressure Fx against the second adjustment ring 200b₂The pressure Fx₂The axial force F2 received by the portion of the back face of the second impeller 120b opposite the second adjustment ring 200b is in the same magnitude and opposite direction, so the force Fx₂Part of the axial force F2 borne by the back of the second impeller 120b is counteracted, and thus the stress area of the second impeller 120b can be reduced, and the effect of reducing the axial force is achieved.

Alternatively, the axial dimension of the second gap 190b is ≧ 0.6 mm.

Further, in some embodiments of the present invention, as shown in FIG. 1, the second radial bearing 160b is secured within the housing 130 by a second bearing seat 180 b.

In some embodiments of the present invention, as shown in fig. 1, a fifth step surface is disposed on the inner wall of the housing 130; the second bearing seat 180b abuts between the second diffuser 140b and the fifth step surface. Thus, the second bearing housing 180b is easily assembled and disassembled.

In some embodiments of the present invention, as shown in fig. 1, a sixth step surface is disposed at the second opening of the housing 130, and a seventh step surface is disposed on an outer wall of the second diffuser 140 b; the seventh step surface is overlapped on the sixth step surface through a fastener. According to the fixing manner of the second diffuser 140b, the second diffuser 140b and the second opening of the housing 130 can be kept flush, so that excessive parts of the second diffuser 140b are prevented from extending into the second volute 150b, and the compressed gas can smoothly flow out from the second gas outlet 152b of the second volute 150 b.

In some embodiments of the present invention, as shown in fig. 1, an eighth step surface is disposed on an outer wall of the rotor 111 of the motor 110; the second adjustment ring 200b abuts the eighth step surface. In this manner, the degree of coupling securement of the second adjusting ring 200b on the rotor 111 of the motor 110 may be improved.

As can be seen from the above description, during the process that the rotor 111 of the motor 110 drives the first impeller 120a and the second impeller 120B to rotate, the back portions of the first impeller 120a and the second impeller 120B are subjected to the axial force generated between the respective gas compression regions B1, B2 and the gas compression regions a1, a2, and the axial force generated by the pressure difference between the compressed gas and the inner cavity of the motor 110 is also generated by the first impeller 120a and the second impeller 120B due to their own structures, so that the axial force of the compressor body is complicated and varied, the direction of the final total axial force is not determined, and it may be that the axial force is directed from the primary shaft to the secondary shaft (i.e. from the first impeller 120a to the second impeller 120B), or may be directed from the secondary shaft to the primary shaft (i.e. from the second impeller 120B to the first impeller 120a), when the axial force is directed to the first impeller 120a, a dynamic pressure gas film is formed in the small gap between the thrust disk 172 and the first axial bearing 171, for supporting axial forces. Similarly, when the axial force is directed to the second impeller 120b, a dynamic pressure film is formed on the surface of the second axial bearing 173.

The invention can effectively reduce the total axial force by the cooperation of the back-rest impeller and the double adjusting ring, thereby ensuring that the bearing is in a safety coefficient range and greatly reducing the risk of bearing failure. The outer diameter of the adjusting ring needs to be designed according to different working conditions, the pressure difference under different working conditions is different, the generated axial force is different, and the outer diameters of the adjusting rings are different in size.

The gas suspension compressor realizes the gas compression process through the structures such as an impeller, a diffuser, a volute and the like. In the process of compressing gas by the impeller, because of the pressure difference existing before and after the refrigerant gas is compressed and the structure that the impeller compresses the gas, the impeller can be subjected to the axial force in the horizontal direction, and the axial force direction points to the refrigerant before the refrigerant gas is compressed after the refrigerant gas is compressed, so that the rotor can be caused to move in the horizontal direction. The larger the rotor play amplitude is, the poorer the operational reliability of the air suspension compressor is.

In the related technology, the axial bearing with larger bearing capacity is used for offsetting and adjusting the axial force, the method has higher requirements on the type selection of the bearing, and the bearing is easy to fail.

The gas bearing drives the thrust disc by utilizing the high-speed rotation of the rotor, a gas film is formed on the surface of the gas bearing after the thrust disc reaches a certain rotating speed, the effect of supporting axial force is realized by utilizing the gas film, and the higher the rotating speed is, the larger the bearing capacity of the gas film is. The greater the axial load, the smaller the gas film thickness, and the greater the likelihood of bearing failure. Therefore, once the axial force exceeds the air film bearing capacity, the bearing is easy to fail. Therefore, the axial load needs to be controlled within the safety factor of the gas bearing, and the normal work of the bearing is ensured.

Based on this, some embodiments of the present disclosure provide a gas suspension compressor, which can further balance the axial force of the compressor and alleviate the problem of large axial movement of the rotor.

As shown in fig. 1, in some embodiments, the air-suspension compressor includes a housing 130, a rotor 111, a first impeller 120a, and a second impeller 120 b.

The rotor 111 is rotatably provided in the housing 130.

The first impeller 120a is disposed at a first axial end of the rotor 111, and the first impeller 120a is configured to rotate with the rotor 111 to form a first pre-gas compression region a1 in front of the first impeller 120a and a first post-gas compression region B1 behind the first impeller 120 a. The front of the first impeller 120a is away from the axial middle of the housing 130 with respect to the rear of the first impeller 120 a.

The second impeller 120B is provided at a second axial end of the rotor 111, and the second impeller 120B is configured to rotate with the rotor 111 to form a second gas compression front region a2 in front of the second impeller 120B and a second gas compression rear region B2 behind the second impeller 120B. The front of the second impeller 120b is distant from the axial middle of the housing 130 with respect to the rear of the second impeller 120 b.

The first axial end and the second axial end are two ends opposite to each other in the axial direction of the rotor 111.

The first adjusting ring 200a is disposed at a first axial end of the rotor 111 and is close to an axial middle portion of the housing 130 relative to the first impeller 120a, the first adjusting ring 200a is configured to rotate with the rotor 111, a first gap 190a is formed between the first adjusting ring 200a and the first impeller 120a, the first gap 190a is located in the first gas compression region B1, and the first adjusting ring 200a is configured to counteract a portion of an axial force generated by a gas pressure difference between the first gas compression region a1 and the first gap 190 a.

A second adjustment ring 200B is disposed at a second axial end of the rotor 111 near an axial middle portion of the housing 130 relative to the second impeller 120B, the second adjustment ring 200B configured to rotate with the rotor 111, a second gap 190B is formed between the second adjustment ring 200B and the second impeller 120B, the second gap 190B is located in a second post-gas-compression region B2, and the second adjustment ring 200B is configured to counteract a portion of an axial force generated by a gas pressure differential between the second pre-gas-compression region a2 and the second gap 190B.

In the above embodiment, the first impeller 120a and the second impeller 120b are disposed back to back and disposed at two axial ends of the rotor 111 respectively, and the axial forces are offset by using the method that the gas pressures applied to the first impeller 120a and the second impeller 120b are opposite to each other, so as to weaken the axial forces and avoid the accumulation of the axial forces of the gas suspension compressor.

After the impeller rotates to compress refrigerant gas, two areas exist: a gas pre-compression region and a gas post-compression region. The pressure of the refrigerant gas before and after compression is different, the pressure difference can generate pressure, and the direction of the force is that the compressed region points to the region before compression.

Referring to fig. 1, the gas compression front regions a1, a2 are far from the axial middle of the housing 130 relative to the gas compression rear regions B1, B2, so that the pressure on the back surfaces of the first impeller 120a and the second impeller 120B is obtained, and by providing the first adjusting ring 200a at the first axial end of the rotor 111 and the second adjusting ring 200B at the second axial end of the rotor 111, the force bearing areas of the back surfaces of the first impeller 120a and the second impeller 120B can be adjusted by the adjusting rings to reduce the force bearing areas of the impellers and further reduce the axial force. Through using back of the body impeller structure + two regulating ring structures, but to a great extent reduces the axial force, improves bearing air film thickness and bearing factor of safety. And because the axial force that rotor 111 received is complicated changeable, final total axial force direction is uncertain, adopts two adjustable rings to adopt single adjustable ring for, the axial force that improves offsets more than the twice, is applicable to the complicated changeable pressure environment in the compressor better.

In some embodiments, the axial dimension of the first gap 190a is greater than or equal to 0.6mm, taking into account the safety of the compressor operation, combined with the axial bearing assembly, the axial load, and the amount of deformation of the axial bearing for the aero-levitation compressor.

In some embodiments, the axial dimension of the second gap 190b is greater than or equal to 0.6mm, taking into account the safety of the compressor operation, combined with the axial bearing assembly, the axial load, and the amount of deformation of the axial bearing for the aero-levitation compressor.

Optionally, the housing 130 is an irregular cavity component, generally cast, for supporting, protecting, and damping purposes.

In some embodiments, a motor cavity 131 is formed within the housing 130. The motor cavity 131 is located between the first and second axial ends of the rotor 111.

A stator 112 is arranged in the motor cavity. The stator 112 is formed of a winding, is fixed inside the housing 130, and provides a magnetic field to the rotor 111.

The rotor 111 is a shaft or a solid part, and performs high-speed rotation motion in a magnetic field provided by the stator 112 during operation.

In some embodiments, the gas pressure within the motor cavity 131 acts on the first adjustment ring 200a, the first adjustment ring 200a configured to counteract a portion of the axial force generated by the first gas pre-compression region a1, the first gap 190a, and the gas pressure differential within the motor cavity 131.

In some embodiments, the gas pressure within the motor cavity 131 acts on the second adjustment ring 200b, the second adjustment ring 200b configured to counteract a portion of the axial force generated by the second gas pre-compression region a2, the second gap 190b, and the gas pressure differential within the motor cavity 131.

According to the embodiment, the adjusting ring can also adjust the pressure generated by the pressure difference between the compressed refrigerant gas and the motor cavity, the direction of the force is that the compressed air cavity points to the motor cavity, and the stress area of the adjusting ring is the area of the adjusting ring.

As can be seen from the above embodiments, the axial force of the compressor is complicated and variable, the final total axial force direction is not determined, and may be directed from the primary shaft (the first impeller 120a) to the secondary shaft, or may be directed from the secondary shaft (the second impeller 120b) to the primary shaft (the first impeller 120a), and the problem of the large axial force is alleviated by disposing the first adjusting ring 200a at a position adjacent to the first impeller 120a, and disposing the second adjusting ring 200b at a position adjacent to the second impeller 120b, so as to reduce the axial load of the impellers through the back-to-back impellers and the double adjusting rings.

In some embodiments, the outer diameter of the first adjustment ring 200a is less than or equal to the outer diameter of the first impeller 120 a.

In some embodiments, the outer diameter of the second adjustment ring 200b is less than or equal to the outer diameter of the second impeller 120 b.

Through the force analysis of the air suspension compressor shown in fig. 1, the generation of the axial force includes the following conditions:

1) the impeller compresses the axial force generated by the pressure difference before and after the refrigerant, and the force direction is the direction before compression after compression.

2) The impeller rotates, the axial force generated by the structure of the impeller is not specified in the direction and is determined by the molded line of the impeller.

3) The compressed air cavity of the refrigerant gas points to the motor cavity.

It can be known from the above axial force generation situation that the synthesis of the axial force of the rotor 111 is complicated, and the total axial force magnitude and direction under different working conditions are also different. Two adjustable rings cooperation adjustable two power: and adjusting the axial force of the pressure difference between the compressed refrigerant gas and the compressed refrigerant gas to the impeller, and adjusting the axial force of the pressure difference between the compressed refrigerant gas and the motor cavity to the adjusting ring. Therefore, the outer diameter of the adjusting ring needs to be designed according to different working conditions, the pressure difference under different working conditions is different, the generated axial force is different, and the outer diameters of the adjusting rings are different in size.

In some embodiments, the aero-levitation compressor further includes a ring-shaped first diffuser 140a, and a first comb sealing structure 210a, an outer circumference of the first diffuser 140a is connected to an inner wall of the casing 130, and the first comb sealing structure 210a is disposed between an inner circumference of the first diffuser 140a and the first adjusting ring 200 a. The motor chamber 121 and the first gas-compressed area B1 are sealed by the first comb-tooth seal structure 210 a.

In some embodiments, the material hardness of the first adjustment ring 200a is greater than the material hardness of the first diffuser 140a to prevent dry friction and seizure of the first adjustment ring 200a with the mating first diffuser 140a during rotation of the rotor 111.

In some embodiments, the aero-levitation compressor further includes a second diffuser 140b having an annular shape, and a second comb sealing structure 210b, an outer circumference of the second diffuser 140b being connected to an inner wall of the casing 130, the second comb sealing structure 210b being disposed between an inner circumference of the second diffuser 140b and the second adjusting ring 200 b. The motor chamber 121 and the second gas-compressed area B2 are sealed by the second comb seal structure 210B.

In some embodiments, the material hardness of the second tuning ring 200b is greater than the material hardness of the second diffuser 140b to prevent dry friction seizure of the second tuning ring 200b with the mating second diffuser 140b during rotation of the rotor 111.

In some embodiments, the air suspension compressor further includes an axial bearing assembly 170, the axial bearing assembly 170 being located at a first axial end of the rotor 111 and near an axial middle of the housing 130 relative to the first adjustment ring 200 a. The rotor 111 axial forces are balanced by the provision of an axial bearing assembly 170.

In some embodiments, the inner diameter of the axial bearing assembly 170 is the same as the inner diameter of the first adjustment ring 200a, and the outer diameter of the axial bearing assembly 170 is greater than the outer diameter of the first adjustment ring 200 a.

In some embodiments, the axial bearing assembly 170 includes a thrust disk 172, a first axial bearing 171, and a second axial bearing 173.

The thrust disk 172 is provided to the rotor 111 and is configured to rotate with the rotor 111.

The first axial bearing 171 is located between the thrust disc 172 and the first adjustment ring 200 a.

The second axial bearing 173 is located on the side of the thrust disk 172 remote from the first axial bearing 171.

In some embodiments, the air-suspension compressor further comprises a first radial bearing 160a, the first radial bearing 160a being located at a first axial end of the rotor 111 and near an axial middle of the housing 130 relative to the axial bearing assembly 170. The radial force experienced by the rotor 111 is adjusted by providing the first radial bearing 160 a.

In some embodiments, the air suspension compressor further includes a first bearing seat 180a, the first bearing seat 180a is connected to an inner wall of the housing 130, and the first radial bearing 160a is disposed on the first bearing seat 180 a.

The outer circumference of the first diffuser 140a is connected to the inner wall of the housing 130, and the first adjusting ring 200a is located between the inner circumference of the first diffuser 140a and the rotor 111.

The axial bearing assembly 170 is located between the first diffuser 140a and the first bearing seat 180a, and the structure is compact.

In some embodiments, a thrust disk 172 is provided to the rotor 111 and is configured to rotate with the rotor 111. The first axial bearing 171 is located between the thrust disc 172 and the first adjusting ring 200a, and is connected to the first diffuser 140 a. The second axial bearing 173 is located between the thrust disk 172 and the first bearing seat 180a, and is connected to the first bearing seat 180 a.

The thrust disk 172 is fixed to the rotor 111, and the rotor 111 drives the thrust disk 172 to rotate at a high speed, so that when the axial force moves toward the first impeller 120a, a small gap between the thrust disk 172 and the first axial bearing 171 forms a dynamic pressure film for supporting the axial force. Similarly, when the axial force moves toward the second impeller 120b, a dynamic pressure film is formed on the surface of the second axial bearing 173 to support the axial force.

In some embodiments, a third gap is formed between the first diffuser 140a and the first bearing seat 180a near the rotor 111, the axial bearing assembly 170 is located in the third gap, and the first diffuser 140a and the first bearing seat 180a far away from the rotor 111 are attached to each other, so that the structure is compact, the axial space of the rotor 111 is not excessively occupied, and the rotor 111 is prevented from being too long.

In some embodiments, the rotor 111 includes a first shaft segment having a diameter smaller than a diameter of a second shaft segment, the first adjustment ring 200a and the axial bearing assembly 170 located at the first shaft segment, and the first radial bearing 160a located at the second shaft segment. The axial bearing assembly 170 is axially limited by the first adjustment ring 200a and the step between the first and second shaft segments.

In some embodiments, the air-suspension compressor further includes a second radial bearing 160b, the second radial bearing 160b being located at a second axial end of the rotor 111 and near an axial middle of the housing 130 relative to the second adjustment ring 200 b.

In some embodiments, the aero-levitation compressor further includes a second diffuser 140b, an outer circumference of the second diffuser 140b is connected to an inner wall of the housing 130, and a second adjusting ring 200b is located between an inner circumference of the second diffuser 140b and the rotor 111.

In some embodiments, the air suspension compressor further includes a second bearing housing 180b, the second bearing housing 180b is connected to an inner wall of the housing 130, and the second radial bearing 160b is disposed on the second bearing housing 180 b; the second bearing block 180b is attached to the second diffuser 140b, so that the internal structure of the air suspension compressor is compact and the overall length is shortened.

The first bearing seat 180a and the second bearing seat 180b are machined parts, and are fixed in the housing 130, and mainly play a role in fixing and supporting.

In some embodiments, the rotor 111 has shaft segments of different diameters, and the diameter of the shaft segment of the rotor 111 where the second adjustment ring 200b is located is less than the diameter of the shaft segment of the rotor 111 where the second radial bearing 160b is located.

In some embodiments, the gas suspension compressor further includes a first volute 150a, the first volute 150a being disposed at the first axial end of the housing 130 and surrounding the first impeller 120a, the first pre-gas compression region a1 and the first post-gas compression region B1 being located within the first volute 150a and being in communication with each other. The first pre-gas compression zone a1 and the first post-gas compression zone B1 form a first pre-gas compression chamber and a first post-gas compression chamber, respectively, within the first volute 150 a.

In some embodiments, the aero-levitation compressor further comprises a second volute 150B, the second volute 150B is disposed at the second axial end of the housing 130 and surrounds the second impeller 120B, and the second pre-gas-compression region a2 and the second post-gas-compression region B2 are located within the second volute 150B and are in communication with each other. The second pre-gas compression region a2 and the second post-gas compression region B2 form a second pre-gas compression chamber and a second post-gas compression chamber, respectively, within the second volute 150B.

Some specific embodiments of the gas suspension compressor are described below with reference to fig. 1 to 4.

As shown in fig. 1, the rotor 111 is rotatably disposed in the housing 130, a first axial end of the housing 130 is provided with a first volute 150a, and a second axial end of the housing 130 is provided with a second volute 150 b. The first axial end and the second axial end are opposite ends of the housing 130 in the axial direction of the rotor 111.

A first axial end of the rotor 111 is provided with a first impeller 120a, the first impeller 120a is located in the first volute 150a, and a first gas compression front area a1 and a first gas compression rear area B1 formed by the first impeller 120a correspond to a first gas compression front chamber and a first gas compression rear chamber in the first volute 150a, respectively. The first scroll casing 150a is provided with a first gas inlet 151a and a first gas outlet 152a, the first gas inlet 151a is communicated with the first gas compression front chamber, and the first gas outlet 152a is communicated with the first gas compression rear chamber.

The second axial end of the rotor 111 is provided with a second impeller 120b, and the second impeller 120b is located within a second volute 150 b. The second impeller 120B forms a second gas compression front region a2 and a second gas compression rear region B2 corresponding to the second gas compression front chamber and the second gas compression rear chamber in the second scroll 150B, respectively. The second volute 150b is provided with a second gas inlet 151b and a second gas outlet 152b, the second gas inlet 151b is communicated with the second gas compression front cavity, and the second gas outlet 152b is communicated with the second gas compression rear cavity.

A first axial end of the rotor 111 is provided with a first adjusting ring 200a, the first adjusting ring 200a being near an axial middle portion of the housing 130 with respect to the first impeller 120 a. The first diffuser 140a is disposed in the housing 130, and a first comb seal structure 210a is disposed between the first diffuser 140a and the first adjusting ring 200 a. The first diffuser 140a is provided with a first bearing seat 180a at a side close to the axial middle portion of the housing 130, and the first radial bearing 160a is provided at the first axial seat 180 a. An axial bearing assembly 170 is disposed between the first diffuser 140a and the first axial seat 180a near the rotor 111. The axial bearing assembly 170 includes a thrust disk 172, a first axial bearing 171, and a second axial bearing 173. The thrust disk 172 is provided to the rotor 111 and is configured to rotate with the rotor 111. The first axial bearing 171 is located between the thrust disc 172 and the first adjusting ring 200a, and is connected to the first diffuser 140 a. The second axial bearing 173 is located between the thrust disk 172 and the first bearing seat 180a, and is connected to the first bearing seat 180 a.

The second axial end of the rotor 111 is provided with a second adjusting ring 200 b. The second adjustment ring 200b is proximate an axial middle of the housing 130 relative to the second impeller 120 b. The second diffuser 140b is arranged in the housing 130, and a second comb seal structure 210b is arranged between the second diffuser 140b and the second adjusting ring 200 b. The second diffuser 140b is provided with a second axial seat 180b at a side thereof close to the axial middle of the housing 130, and the second radial bearing 160b is provided at the second axial seat 180 b.

The rotor 111 rotates at a high speed, and rotates the first impeller 120 a. When the first impeller 120a rotates at a high speed, the refrigerant gas enters the first volute 150a from the first inlet 151a, and the first impeller 120a compresses the refrigerant gas in cooperation with the first diffuser 140 a. The refrigerant gas compressed by the first impeller 120a and the first diffuser 140a is changed into a high-temperature and high-pressure refrigerant gas.

As shown in fig. 2, a pressure difference is formed between the first pre-gas compression region a1 and the first post-gas compression region B1, and the back of the first impeller 120a receives a horizontal force F1 to push the first impeller 120a in the direction of the first inlet port 151 a.

The first diffuser 140a and the second diffuser 140b are both stators 112 fixed on the inner wall of the housing 130. The first adjusting ring 200a is fixed to a first axial end of the rotor 111, and a first gap 190a between the first adjusting ring 200a and the first impeller 120a is compressed gas, where a minute air chamber is formed. The first adjusting ring 200a rotates along with the rotor 111, and the first adjusting ring 200a can reduce the force-bearing area of the first impeller 120 a.

Since the first impeller 120a and the first adjusting ring 200a are both rotors 111, and rotate along with the rotors 111, the gas will generate forces Fx with the same magnitude and opposite directions on the first impeller 120a and the first adjusting ring 200a, respectively₁The forces will mutually abutAnd (4) eliminating. At this time, the pressure area of the F1 to the first impeller 120a is equal to the area of the first impeller 120a — the area of the first adjusting ring 200 a. Therefore, the force receiving area of the first impeller 120a is adjusted by increasing the outer diameter of the first adjusting ring 200a, and the larger the first adjusting ring 200a is, the smaller F1 is.

As shown in fig. 3, since the pressure in the motor cavity 131 is relatively low, the compressed refrigerant gas generates a pressure difference with the gas in the motor cavity 131, and a pressure Fx is generated to the first adjusting ring 200a₃The force receiving area is the area of the first adjusting ring 200a, and the force direction is directed to the motor cavity 131. The force-bearing area is adjusted by adjusting the size of the first adjusting ring 200a, the smaller the first adjusting ring 200a is, the smaller the force-bearing area is, and the Fx₃The smaller.

From the above, it can be seen that the size of the first adjustment ring 200a affects F1, Fx₃The size of (2). For the selection of the size of the first adjusting ring 200a, specific comprehensive evaluation and selection are required according to compressors with different powers and different working conditions, because different cooling capacities and pressure differences between the impeller cover and the impeller back under different working conditions or pressure differences under different working conditions exist.

Generally, the inner diameter of the first adjusting ring 200a must not be smaller than the outer diameter of the rotor 111 at the fitting, and the outer diameter of the first adjusting ring 200a must not be larger than the outer diameter of the first impeller 120 a.

As shown in fig. 1, the rotor 111 rotates at a high speed, and rotates the second impeller 120 b. When the second impeller 120b rotates at a high speed, the refrigerant gas enters the second volute 150b from the second inlet 151b, and the second impeller 120b compresses the refrigerant gas in cooperation with the second diffuser 140 b. The refrigerant gas compressed by the second impeller 120b and the second diffuser 140b is changed into a high-temperature and high-pressure refrigerant gas.

As shown in fig. 3, similar to the force analysis of the first impeller 120a, a pressure difference is formed between the second pre-gas-compression region a2 and the second post-gas-compression region B2, and the back of the second impeller 120B receives a horizontal force F2 to push the second impeller 120B toward the second inlet 151B.

The second adjusting ring 200b is fixed to the second axial end of the rotor 111, and a second gap 190b between the second adjusting ring 200b and the second impeller 120b is compressed gas, where a minute secondary air chamber is formed. The second adjusting ring 200b rotates along with the rotor 111, and the second adjusting ring 200b may reduce a force-receiving area of the second impeller 120 b.

Since the second impeller 120b and the second adjusting ring 200b are both rotors 111, they follow the rotors 111 for rotation. The gas will generate the same and opposite forces Fx to the second impeller 120b and the second adjusting ring 200b, respectively₂The forces will cancel each other out. At this time, the pressure area of F2 against the second impeller 120b is equal to the area of the second impeller 120b — the area of the second adjustment ring 200 b. Therefore, the force receiving area of the second impeller 120b may be adjusted by increasing the outer diameter of the second adjustment ring 200b, the larger the second adjustment ring 200b, the smaller F2.

As can be seen, the force analysis of the second adjustment ring 200b is similar to the first adjustment ring 200 a.

By the back-to-back first impeller 120a and second impeller 120b, F1 is in the opposite direction to F2, and to some extent, can counteract some of the axial force, reducing it.

The materials of the first adjusting ring 200a and the second adjusting ring 200b should be selected to be slightly harder than the materials of the diffusers at the corresponding positions, and the difference between the hardness of the two materials is generally more than or equal to 15HRC, so as to prevent the adjusting rings from seizing up with the matched diffusers due to dry friction during the rotation of the rotor 111.

Considering the safety of the compressor operation, the axial bearing assembly structure, the axial load and the deformation of the axial bearing for the gas suspension compressor are integrated, and the distance between the impeller and the diffuser and the distance between the impeller and the adjusting ring are more than or equal to 0.6 mm.

To sum up, the back-to-back impeller and the double adjusting ring axial load composite matching structure can reduce the axial force of the rotor 111, reduce the axial bearing load and thicken the bearing air film, so that the bearing is in the safety coefficient range, and the risk of bearing failure is greatly reduced.

Some embodiments of the invention further provide a refrigeration device comprising the gas suspension compressor in any of the above embodiments.

In the air suspension compressor in the above embodiment, the rotor 111 of the motor 110 is sleeved with the adjusting ring, the adjusting ring is located in the gas compression regions B1 and B2 and has an adjusting gap (the first gap 190a and the second gap 190B) with the impeller, when the rotor 111 of the motor 110 drives the adjusting ring and the impeller to rotate, the gas in the adjusting gap generates a pressure on the adjusting ring, the pressure is opposite to and the same as the direction and the magnitude of the axial force received by the portion of the back surface of the impeller, which is opposite to the adjusting ring, so that the partial axial force generated by the gas pressure difference between the gas compression regions B1 and B2 and the gas compression regions a1 and a2 can be offset, and a gas film formed by the axial bearing assembly 170 is ensured to have a certain thickness, thereby reducing the probability of failure of the axial bearing assembly 170, and improving the operation reliability of the air suspension compressor.

As an example, the refrigeration device according to the present invention may be an electric appliance such as an air conditioner or a refrigerator.

Based on the embodiments of the invention described above, the technical features of one of the embodiments can be advantageously combined with one or more other embodiments without explicit negatives.

Finally, it should be noted that the above examples are only used to illustrate the technical solutions of the present invention and not to limit the same; although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art will understand that: modifications to the specific embodiments of the invention or equivalent substitutions for parts of the technical features may be made; without departing from the spirit of the present invention, it is intended to cover all aspects of the invention as defined by the appended claims.

Claims

1. A gas suspension compressor, comprising:

a housing (130);

a rotor (111) rotatably provided in the housing (130);

a first impeller (120a) provided at a first axial end of the rotor (111), the first impeller (120a) being configured to rotate to form a first pre-gas-compression region (A1) in front of the first impeller (120a) and a first post-gas-compression region (B1) behind the first impeller (120 a);

a second impeller (120B) provided at a second axial end of the rotor (111), the second impeller (120B) being configured to rotate so as to form a second pre-gas-compression region (A2) in front of the second impeller (120B) and a second post-gas-compression region (B2) behind the second impeller (120B);

a first adjusting ring (200a) provided at a first axial end of the rotor (111), the first adjusting ring (200a) forming a first gap (190a) with the first impeller (120a), the first gap (190a) being located in the first post-gas-compression region (B1), the first adjusting ring (200a) being configured to counteract a portion of an axial force generated by a gas pressure differential within the first pre-gas-compression region (a1) and the first gap (190 a); and

a second adjustment ring (200B) provided at a second axial end of the rotor (111), the second adjustment ring (200B) forming a second gap (190B) with the second impeller (120B), the second gap (190B) being located in the second post-gas-compression region (B2), the second adjustment ring (200B) being configured to counteract a portion of an axial force generated by a gas pressure differential within the second pre-gas-compression region (A2) and the second gap (190B).

2. Gas suspension compressor according to claim 1, characterized in that a motor cavity (131) is formed in said housing (130);

the gas pressure within the motor cavity (131) acts on the first adjusting ring (200a), the first adjusting ring (200a) being configured to counteract a portion of an axial force generated by the first gas pre-compression region (A1), the first gap (190a), and the gas pressure differential within the motor cavity (131), and/or,

the gas pressure within the motor cavity (131) acts on the second adjustment ring (200b), the second adjustment ring (200b) being configured to counteract a portion of the axial force generated by the second gas pre-compression region (A2), the second gap (190b), and the gas pressure differential within the motor cavity (131).

3. Gas suspension compressor according to claim 1, characterized in that the first adjusting ring (200a) has an outer diameter less than or equal to the outer diameter of the first impeller (120a) and/or the second adjusting ring (200b) has an outer diameter less than or equal to the outer diameter of the second impeller (120 b).

4. The air-suspension compressor of claim 1, further comprising:

an annular first diffuser (140a) and a first comb seal structure (210a), an outer periphery of the first diffuser (140a) being connected to an inner wall of the housing (130), the first comb seal structure (210a) being provided between an inner periphery of the first diffuser (140a) and the first adjusting ring (200a), and/or,

annular second diffuser (140b) and second broach seal structure (210b), the periphery of second diffuser (140b) is connected in the inner wall of casing (130), second broach seal structure (210b) are located the inner periphery of second diffuser (140b) with between second adjustable ring (200 b).

5. The gas suspension compressor of claim 1, further comprising an axial bearing assembly (170), the axial bearing assembly (170) being located at a first axial end of the rotor (111) and proximate an axial middle of the housing (130) relative to the first adjustment ring (200 a).

6. The gas suspension compressor of claim 5, wherein the axial bearing assembly (170) has an inner diameter that is the same as an inner diameter of the first adjustment ring (200a), and the axial bearing assembly (170) has an outer diameter that is greater than an outer diameter of the first adjustment ring (200 a).

7. The gas suspension compressor according to claim 5, wherein the axial bearing assembly (170) comprises:

a thrust disk (172) provided to the rotor (111);

a first axial bearing (171) located between the thrust disc (172) and the first adjustment ring (200 a); and

a second axial bearing (173) located on a side of the thrust disk (172) remote from the first axial bearing (171).

8. The gas suspension compressor of claim 5, further comprising a first radial bearing (160a), the first radial bearing (160a) being located at a first axial end of the rotor (111) and near an axial middle of the housing (130) relative to the axial bearing assembly (170).

9. The air-suspension compressor of claim 8, further comprising:

a first diffuser (140a) having an outer circumference connected to an inner wall of the housing (130), the first adjusting ring (200a) being located between an inner circumference of the first diffuser (140a) and the rotor (111); and

a first bearing seat (180a) connected to an inner wall of the housing (130), the first radial bearing (160a) being provided to the first bearing seat (180 a);

wherein the axial bearing assembly (170) is located between the first diffuser (140a) and the first bearing seat (180 a).

10. The air-suspension compressor of claim 9, wherein the axial bearing assembly (170) includes a thrust disk (172), a first axial bearing (171), and a second axial bearing (173); the thrust disc (172) is arranged on the rotor (111); the first axial bearing (171) is located between the thrust disc (172) and the first adjusting ring (200a) and is connected to the first diffuser (140 a); the second axial bearing (173) is located between the thrust disk (172) and the first bearing seat (180a), and is connected to the first bearing seat (180 a).

11. The compressor of claim 9, wherein a third gap is formed between the first diffuser (140a) and the first bearing seat (180a) at a position close to the rotor (111), the axial bearing assembly (170) is located at the third gap, and the first diffuser (140a) and the first bearing seat (180a) are attached to each other at a position far from the rotor (111).

12. The gas suspension compressor of claim 8, wherein the rotor (111) includes a first shaft section and a second shaft section, the first shaft section having a diameter smaller than the second shaft section, the first adjusting ring (200a) and the axial bearing assembly (170) being located at the first shaft section, the first radial bearing (160a) being located at the second shaft section.

13. Gas suspension compressor according to claim 1, further comprising a second radial bearing (160b), said second radial bearing (160b) being located at a second axial end of the rotor (111) and close to the axial middle of the housing (130) with respect to the second adjusting ring (200 b).

14. The air-suspension compressor of claim 13, further comprising:

a second diffuser (140b) having an outer circumference connected to an inner wall of the housing (130), the second diffuser (140b) being located between an inner circumference of the second diffuser (140b) and the rotor (111); and

a second bearing housing (180b) coupled to an inner wall of the housing (130), the second radial bearing (160b) being disposed on the second bearing housing (180 b); the second bearing seat (180b) is attached to the second diffuser (140 b).

15. Gas suspension compressor according to claim 13, characterized in that said rotor (111) has shaft sections of different diameters, the diameter of the section of the rotor (111) where said second adjusting ring (200b) is located being smaller than the diameter of the section of the rotor (111) where said second radial bearing (160b) is located.

16. The air-suspension compressor of claim 1, further comprising:

a first volute (150a) disposed at a first axial end of the housing (130) and surrounding the first impeller (120a), the first pre-gas compression zone (A1) and the first post-gas compression zone (B1) being located within the first volute (150a) and communicating with each other; and/or the presence of a gas in the gas,

a second volute (150B) disposed at a second axial end of the housing (130) and surrounding the second impeller (120B), the second pre-gas-compression region (A2) and the second post-gas-compression region (B2) being located within the second volute (150B) and communicating with each other.

17. The gas suspension compressor according to claim 4,

the material hardness of the first adjusting ring (200a) is greater than the material hardness of the first diffuser (140 a); and/or the presence of a gas in the gas,

the material hardness of the second adjusting ring (200b) is greater than the material hardness of the second diffuser (140 b).

18. The gas suspension compressor of claim 17,

the difference between the material hardness of the first adjusting ring (200a) and the material hardness of the first diffuser (140a) is more than or equal to 15 HRC; and/or the presence of a gas in the gas,

the difference between the material hardness of the second adjusting ring (200b) and the material hardness of the second diffuser (140b) is larger than or equal to 15 HRC.

19. Gas suspension compressor according to claim 1, characterized in that the axial dimension of said first interspace (190a) is greater than or equal to 0.6mm and/or the axial dimension of said second interspace (190b) is greater than or equal to 0.6 mm.

20. A gas suspension compressor, comprising:

a compressor body having a gas pre-compression region and a gas post-compression region in communication within the compressor body, the compressor body including a rotor (111) and an impeller; and

an adjusting ring mounted on the rotor (111) and having an adjusting gap with the impeller in the post-gas compression region to offset a portion of the axial force between the post-gas compression region and the pre-gas compression region generated by the gas pressure differential;

21. A gas suspension compressor, comprising:

the compressor comprises a compressor body, a compressor body and a compressor body, wherein the compressor body is internally provided with a gas compression front area and a gas compression rear area which are communicated with each other, and the compressor body comprises a rotor (111), an impeller and a diffuser; and

22. The gas suspension compressor of claim 21, wherein the difference between the hardness of the material of the adjusting ring and the hardness of the material of the diffuser is greater than or equal to 15 HRC.

23. A gas suspension compressor, comprising:

wherein the axial size of the adjusting gap is more than or equal to 0.6 mm;

24. The gas suspension compressor of claim 23, wherein the difference between the hardness of the material of the adjusting ring and the hardness of the material of the diffuser is greater than or equal to 15 HRC.

25. Refrigeration plant, characterized in that it comprises a gas suspension compressor according to any one of claims 1 to 24.