CN216617931U - A kind of compressor - Google Patents

Abstract

The application relates to the technical field of gas compression, concretely relates to compressor includes: a housing and a rotor; a low-pressure cavity, a compression cavity and a high-pressure cavity are sequentially formed between the rotor and the shell along the axial direction; the rotor is provided with a balance hub at the high-pressure cavity, so that high-pressure gas flowing out of the compression cavity provides a first balance force from the low-pressure cavity to the high-pressure cavity to the rotor through the balance hub; be provided with the atress portion on the rotor, be formed with balanced chamber between atress portion and the casing, along the axial of rotor, balanced chamber is located one side that the low pressure chamber deviates from the compression chamber, is connected with balanced pipe between high pressure chamber and the balanced chamber for partial high-pressure gas in the high pressure chamber flows into balanced chamber through balanced pipe, and provides the second balanced power by low pressure chamber to high pressure chamber direction to the rotor through the atress portion. Through the mode, the axial force of the rotor in the compressor can be balanced, and the rotor can run more stably and reliably.

Description

A kind of compressor

Technical Field

The application relates to the technical field of gas compression, in particular to a compressor.

Background

The compressor is a driven fluid machine for lifting low-pressure gas into high-pressure gas, and comprises an axial flow compressor, wherein the axial flow compressor is a turbo-mechanical device for providing compressed gas, and when the axial flow compressor operates, blades do work on the gas to increase the pressure of the gas.

In the operation process of the axial flow compressor, the high-pressure gas at the exhaust end can form axial thrust from the high-pressure end to the low-pressure end on the rotor, and the axial thrust on the rotor is generally counteracted by arranging structures which are mutually abutted and rubbed on the rotor and the shell in the conventional axial flow compressor, so that the structures which are mutually abutted and rubbed are easily abraded and thermally deformed, and the operation stability of the rotor is influenced.

SUMMERY OF THE UTILITY MODEL

In view of the above problems, the present application provides a compressor, so as to balance the axial force of the rotor in the compressor, and make the operation of the rotor more stable and reliable.

The application provides a compressor, includes: a housing and a rotor; the rotor is arranged on the shell in a penetrating manner, a low-pressure cavity, a compression cavity and a high-pressure cavity are sequentially formed between the rotor and the shell along the axial direction, and when the rotor rotates relative to the shell, low-pressure gas in the low-pressure cavity flows into the compression cavity to be compressed to form high-pressure gas and then enters the high-pressure cavity; the rotor is provided with a balance hub at the high-pressure cavity, so that high-pressure gas flowing out of the compression cavity provides a first balance force from the low-pressure cavity to the high-pressure cavity to the rotor through the balance hub; be provided with the atress portion on the rotor, be formed with balanced chamber between atress portion and the casing, along the axial of rotor, balanced chamber is located one side that the low pressure chamber deviates from the compression chamber, is connected with balanced pipe between high pressure chamber and the balanced chamber for partial high-pressure gas in the high pressure chamber flows into balanced chamber through balanced pipe, and provides the second balanced power by low pressure chamber to high pressure chamber direction to the rotor through the atress portion.

In an alternative mode, the balance hub comprises a cylindrical section and a table body section with a side edge being a straight line, the table body section is located between the cylindrical section and the compression cavity along the axial direction of the rotor, and the diameter of the table body section gradually increases from one end close to the compression cavity to the other end.

In an alternative mode, the balance hub comprises a cylindrical section and a table section with arc-shaped side edges, the table section is located between the cylindrical section and the compression cavity along the axial direction of the rotor, and the diameter of the table section is gradually increased from one end close to the compression cavity to the other end.

In an alternative form, the cylindrical section is sealingly connected to the housing.

In an optional mode, the stress part comprises a first step and a second step, the first step and the second step are both connected with the shell in a sealing mode, and a balance cavity is formed among the first step, the second step and the shell; the high pressure gas in the balance chamber provides a second balance force for the rotor by applying a force from the low pressure chamber to the high pressure chamber to a face of the second step adjacent to the first step.

In an alternative mode, the shell comprises a sealing shaft sleeve, the sealing shaft sleeve is respectively connected with the first step and the second step in a sealing mode, and a balance cavity is formed among the sealing shaft sleeve, the first step and the second step.

In an optional mode, the shell further comprises a butting wall, the butting wall is butted with the sealing shaft sleeve, a buffer cavity is formed inside the butting wall, and the balance pipe is communicated with the buffer cavity; the abutting wall and the sealing shaft sleeve are provided with vent holes, and the buffer cavity is communicated with the balance cavity through the vent holes.

In an alternative mode, the balance pipe is provided with a regulating valve.

In an alternative mode, the housing is provided with a thrust bearing, and the rotor is provided with a thrust disc which is matched and connected with the thrust bearing and used for limiting the axial displacement of the rotor.

In an alternative mode, a bearing is arranged on the shell, and two ends of the rotor are connected with the bearing in a matched mode.

This application is through setting up balanced hub with the rotor in high-pressure chamber department for the high-pressure gas that flows out in the compression chamber can exert the thrust by low pressure chamber to high-pressure chamber direction to balanced hub, thereby provide the first balance force by low pressure chamber to high-pressure chamber direction to the rotor, because first balance force and above-mentioned axial thrust all act on the rotor and opposite direction, according to the interact of power, a part axial thrust can be offset to first balance force, make rotor axial atress reduce, promote structural stability. This application still sets up the atress portion on the rotor, form balanced chamber between atress portion and the casing, balanced chamber is through balance pipe and high-pressure chamber intercommunication, make high-pressure gas in the high-pressure chamber can reach in the balanced chamber and exert the thrust by low pressure chamber to high-pressure chamber direction to the atress portion, thereby provide the second balancing force by low pressure chamber to high-pressure chamber direction to the rotor, combine together through first balancing force and second balancing force and offset the axial thrust of rotor jointly, thereby more balanced rotor is to the ascending effort of bigger degree, make the structure of rotor more reliable, the operation is more stable.

The foregoing description is only an overview of the technical solutions of the present invention, and the embodiments of the present invention are described below in order to make the technical means of the present invention more clearly understood and to make the above and other objects, features, and advantages of the present invention more clearly understandable.

Drawings

Various other advantages and benefits will become apparent to those of ordinary skill in the art upon reading the following detailed description of the preferred embodiments. The drawings are only for purposes of illustrating the preferred embodiments and are not to be construed as limiting the utility model. Also, like reference numerals are used to refer to like parts throughout the drawings. In the drawings:

FIG. 1 is a schematic cross-sectional view of a compressor according to an embodiment of the present disclosure;

FIG. 2 is a schematic structural diagram of a rotor in a compressor according to an embodiment of the present disclosure;

FIG. 3 is a schematic view of a rotor of a compressor according to another embodiment of the present disclosure;

FIG. 4 is a schematic cross-sectional view of a compressor according to an embodiment of the present disclosure, illustrating a connection between a balance hub and a housing;

FIG. 5 is a schematic cross-sectional view of a compressor according to another embodiment of the present application;

fig. 6 is a schematic cross-sectional view of a compressor according to another embodiment of the present application.

The reference numbers in the detailed description are as follows:

the compressor 100, the housing 110, the low pressure chamber 111, the compression chamber 112, the high pressure chamber 113, the balance chamber 114, the buffer chamber 1141, the inlet port 115, the outlet port 116, the seal connection 117, the seal bushing 118, the abutment wall 119, the vent hole 1191, the rotor 120, the balance hub 121, the cylindrical section 1211, the stage section 1212, the force receiving portion 122, the first step 1221, the second step 1222, the balance tube 130, the regulating valve 131, the thrust bearing 141, the thrust disc 142, and the bearing 150.

Detailed Description

Embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The following examples are merely used to more clearly illustrate the technical solutions of the present application, and therefore are only examples, and the protection scope of the present application is not limited thereby.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs; the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the application; the terms "including" and "having," and any variations thereof, in the description and claims of this application and the description of the above figures are intended to cover non-exclusive inclusions.

In the description of the embodiments of the present application, the technical terms "first", "second", and the like are used only for distinguishing different objects, and are not to be construed as indicating or implying relative importance or implicitly indicating the number, specific order, or primary-secondary relationship of the technical features indicated. In the description of the embodiments of the present application, "a plurality" means two or more unless specifically defined otherwise.

Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment can be included in at least one embodiment of the application. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. It is explicitly and implicitly understood by one skilled in the art that the embodiments described herein can be combined with other embodiments.

In the description of the embodiments of the present application, the term "and/or" is only one kind of association relationship describing an associated object, and means that three relationships may exist, for example, a and/or B, and may mean: there are three cases of A, A and B, and B. In addition, the character "/" herein generally indicates that the former and latter related objects are in an "or" relationship.

In the description of the embodiments of the present application, the term "plurality" refers to two or more (including two), and similarly, "plural sets" refers to two or more (including two), and "plural pieces" refers to two or more (including two).

In the description of the embodiments of the present application, the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", and the like, indicate the directions or positional relationships indicated in the drawings, and are only for convenience of description of the embodiments of the present application and for simplicity of description, but do not indicate or imply that the referred device or element must have a specific direction, be constructed and operated in a specific direction, and thus, should not be construed as limiting the embodiments of the present application.

In the description of the embodiments of the present application, unless otherwise explicitly stated or limited, the terms "mounted," "connected," "fixed," and the like are used in a broad sense, and for example, may be fixedly connected, detachably connected, or integrated; mechanical connection or electrical connection is also possible; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the embodiments of the present application can be understood by those of ordinary skill in the art according to specific situations.

An embodiment of the present application provides a compressor, and specifically, referring to fig. 1, a sectional structure of a compressor 100 according to an embodiment of the present application is shown. The compressor 100 includes: a housing 110 and a rotor 120. The rotor 120 is disposed on the housing 110 in a penetrating manner, a low pressure chamber 111, a compression chamber 112 and a high pressure chamber 113 are sequentially formed between the rotor 120 and the housing 110 along an axial direction, and when the rotor 120 rotates relative to the housing 110, low pressure gas in the low pressure chamber 111 flows into the compression chamber 112 and is compressed to form high pressure gas and then enters the high pressure chamber 113. The rotor 120 is provided with a balance hub 121 at the high pressure chamber 113, so that the high pressure gas flowing out of the compression chamber 112 provides a first balance force to the rotor 120 from the low pressure chamber 111 to the high pressure chamber 113 through the balance hub 121. The rotor 120 is provided with a force receiving portion 122, a balance cavity 114 is formed between the force receiving portion 122 and the casing 110, the balance cavity 114 is located on one side of the low pressure cavity 111, which is away from the compression cavity 112, along the axial direction of the rotor 120, and a balance pipe 130 is connected between the high pressure cavity 113 and the balance cavity 114, so that part of high pressure gas in the high pressure cavity 113 flows into the balance cavity 114 through the balance pipe 130, and a second balance force in the direction from the low pressure cavity 111 to the high pressure cavity 113 is provided to the rotor 120 through the force receiving portion 122.

Specifically, as shown in fig. 1, the arrow direction in the figure indicates the gas flow direction, low-pressure gas enters the low-pressure chamber 111 through the gas inlet 115 on the casing 110, when the rotor 120 rotates, the low-pressure gas in the low-pressure chamber 111 enters the compression chamber 112, moving blades on the rotor 120 and stationary blades in the compression chamber 112 perform work to compress the low-pressure gas in the compression chamber 112 into high-pressure gas, the compressed high-pressure gas enters the high-pressure chamber 113 from the compression chamber 112, wherein most of the high-pressure gas is discharged through the gas outlet 116 on the casing 110 and is subsequently utilized, and a small part of the high-pressure gas enters the balance chamber 114 through the balance pipe 130.

During the gas compression process, due to the difference between the gas pressures in the high pressure chamber 113 and the low pressure chamber 111, the high pressure gas applies an axial thrust to the rotor in the direction from the high pressure chamber 113 to the low pressure chamber 111 (in the x-axis direction in fig. 1).

In order to avoid the influence of the axial thrust on the structure and normal operation of the rotor 120, the balance hub 121 is arranged at the high-pressure cavity 113 of the rotor 120, so that high-pressure gas flowing out of the compression cavity 112 applies thrust in the direction from the low-pressure cavity 111 to the high-pressure cavity 113 (the direction opposite to the x-axis direction in fig. 1) to the balance hub 121, and thus first balance force in the direction from the low-pressure cavity 111 to the high-pressure cavity 113 is provided to the rotor 120. The inventor of the present application found in research that, because the high-pressure gas flowing out of the compression chamber 112 provides a limited thrust to the balance hub 121, that is, the first balance force is limited in magnitude, and thus cannot provide a good balance effect on the axial thrust received by the rotor 120, the present application further provides the force receiving portion 122 on the rotor 120, the force receiving portion 122 forms the balance chamber 114 with the housing 110, the balance chamber 114 is communicated with the high-pressure chamber 113 through the balance pipe 130, so that the high-pressure gas in the high-pressure chamber 113 can reach the balance chamber 114 and apply a thrust in a direction from the low-pressure chamber 111 to the high-pressure chamber 113 (a direction opposite to the x-axis direction in fig. 1) to the force receiving portion 122, thereby providing the second balance force in a direction from the low-pressure chamber 111 to the high-pressure chamber 113 to the rotor 120, and jointly canceling the axial thrust of the rotor 120 through the first balance force and the second balance force, thereby balancing the axial acting force of the rotor 120 to a greater extent, the structure of the rotor 120 is more reliable and the operation is more stable.

In the compressor 100 provided by the application, the air sources for providing the first balance force and the second balance force for the rotor 120 are both from the compressor 100, air is not required to be introduced from the outside of the compressor 100, the components and the structure for providing the balance force are optimized, and the resource consumption is reduced.

With continuing reference to fig. 1 and with further reference to fig. 2, fig. 2 illustrates a structure of a rotor 120 of the compressor 100 according to an embodiment of the present disclosure. In some embodiments of the present application, the balance hub 121 includes a cylindrical section 1211 and a table section 1212 having a straight side edge, the table section 1212 is located between the cylindrical section 1211 and the compression cavity 112 along the axial direction of the rotor 120, and the diameter of the table section 1212 increases from one end near the compression cavity 112 to the other end.

Specifically, the cylindrical section 1211 and the stage section 1212 may be integrated with the rotor 120, or may be sleeved and fixed on the rotor 120.

By providing the cylindrical section 1211 such that the annular side of the cylindrical section 1211 can contact the housing 110 and the contact surface is a horizontal surface, the balance hub 121 is prevented from being in inclined contact with the housing 110, thereby facilitating a sealing connection structure between the annular side of the cylindrical section 1211 and the housing 110 and ensuring sealing performance between the balance hub 121 and the housing 110. By arranging the stage segment 1212 and gradually increasing the diameter of the stage segment 1212 from the end close to the compression cavity 112 to the other end, the high-pressure gas flowing out of the compression cavity 112 applies a thrust to the annular side surface of the stage segment 1212, so as to provide a first balance force for the rotor 120, and compared with the step structure perpendicular to the axial direction of the rotor 120, the stage segment 1212 with the straight side edge can effectively avoid the high-pressure gas flowing out of the compression cavity 112 from flowing back under the action of the vertical surface of the step structure to affect the efficiency of gas compression.

Referring to fig. 3, a structure of a rotor 120 of a compressor 100 according to another embodiment of the present application is shown. In some embodiments of the present application, the balance hub 121 includes a cylindrical section 1211 and a table section 1212 with curved side edges, the table section 1212 is located between the cylindrical section 1211 and the compression cavity 112 along the axial direction of the rotor 120, and the diameter of the table section 1212 increases from one end near the compression cavity 112 to the other end.

Similarly, a sealing connection structure is conveniently arranged between the annular side surface of the cylindrical section 1211 and the housing 110, and is beneficial to ensuring the sealing performance between the balance hub 121 and the housing 110, the high-pressure gas flowing out of the compression cavity 112 applies a thrust force to the annular side surface of the stage body section 1212, so as to provide a first balance force for the rotor 120, and compared with the step structure which is perpendicular to the axial direction of the rotor 120, the stage body section 1212 with the side edge being an arc line can also effectively avoid the high-pressure gas flowing out of the compression cavity 112 from flowing back under the action of the vertical surface of the step structure, so as to influence the efficiency of gas compression.

Further, referring to fig. 4, a structure of the cylindrical section 1211 and the shell 110 in the compressor 100 according to an embodiment of the present application is shown, in which the cylindrical section 1211 and the shell 110 are in a sealed connection.

Since the housing 110 and the balance hub 121 are rigid structures and relative sliding occurs between the balance hub 121 and the housing 110 during the rotation of the rotor 120, the cylindrical section 1211 of the balance hub 121 is in direct contact with the housing 110 to rub against the housing 110, which is poor in sealing effect.

Based on this, as shown in fig. 4, the casing 110 may be provided with a sealing connector 117 at a position corresponding to the cylindrical section 1211, the sealing connector 117 is in frictional sealing connection with the annular side surface of the cylindrical section 1211, the sealing connector 117 may be, for example, a labyrinth seal manner, specifically, the labyrinth seal is that a plurality of annular sealing teeth are arranged in sequence on the annular side surface of the cylindrical section 1211, a series of cut-off gaps and expansion cavities are formed between the teeth, and the high-pressure gas generates a throttling effect when passing through the gaps of the labyrinth to achieve the purpose of leakage prevention.

By hermetically connecting the cylindrical section 1211 with the housing 110, it is possible to effectively prevent high-pressure gas from leaking from a gap between the cylindrical section 1211 and the housing 110.

Referring to fig. 1 and 2 again, the force-receiving portion 122 includes a first step 1221 and a second step 1222, the first step 1221 and the second step 1222 are hermetically connected to the housing 110, a balance chamber 114 is formed between the first step 1221, the second step 1222 and the housing 110, and the high-pressure gas in the balance chamber 114 provides a second balance force for the rotor 120 by applying a force from the low-pressure chamber 111 to the high-pressure chamber 113 to a surface of the second step 1222 adjacent to the first step 1221.

Since the balance chamber 114 is communicated with the high pressure chamber 113, not directly communicated with the compression chamber 112, and the gas pressure in the high pressure chamber 113 is necessarily greater than or equal to the gas pressure in the balance chamber 114, there is no need to consider the backflow problem of the high pressure gas in the balance chamber 114, and based on this, by setting the force receiving portion 122 to the first step 1221 and the second step 1222, the thrust force applied by the high pressure gas in the balance chamber 114 to the second step 1222 is greater, and the thrust force can be effectively maintained, so that a greater second balance force is provided to the rotor 120, so that the forces in the axial direction of the rotor 120 are well balanced, and the structural reliability and the operational stability of the rotor are ensured.

Referring to fig. 5, a sectional view of a compressor 100 according to another embodiment of the present invention is shown. In some embodiments of the present application, the housing 110 further includes a sealing sleeve 118, the sealing sleeve 118 is sealingly connected with the first step 1221 and the second step 1222, respectively, and the sealing sleeve 118, the first step 1221 and the second step 1222 form the balance cavity 114 therebetween.

Similarly, the sealing sleeve 118 and the first and second steps 1221 and 1222 may be sealed by a labyrinth to ensure airtightness in the balance chamber 114, so that the pressure of the high-pressure gas in the balance chamber 114 may sufficiently act on the second step 1222 to provide a good second balance force for the rotor 120 in the axial direction.

Referring to fig. 6, a sectional view of a compressor 100 according to another embodiment of the present application is shown. In some embodiments of the present application, the housing 110 further includes an abutting wall 119, the abutting wall 119 abuts the seal sleeve 118, a buffer cavity 1141 is formed inside the abutting wall 119, and the balance pipe 130 is communicated with the buffer cavity 1141. A vent hole 1191 is formed in each of the abutting wall 119 and the seal sleeve 118, and the vent hole 1191 communicates the buffer chamber 1141 with the balance chamber 114.

As shown in fig. 6, in order to sufficiently ensure the sealing performance between the first step 1221, the second step 1222 and the sealing sleeve 118, the sealing sleeve 118 may be configured to be "Z" shaped, and two parallel sections of the sealing sleeve 118 are respectively connected with the horizontal sides of the first step 1221 and the second step 1222 in a sealing manner, so that on one hand, the sealing contact area between the sealing sleeve 118 and the first step 1221 and the second step 1222 can be increased, thereby improving the sealing performance, and on the other hand, the sealing connection in the horizontal plane facilitates the sealing assembly between the first step 1221, the second step 1222 and the sealing sleeve 118, which is beneficial for improving the assembly efficiency of the compressor 100.

Through setting up butt wall 119 and sealed axle sleeve 118 butt, can strengthen sealed axle sleeve 118's structural stability, and then fully guarantee the sealing performance between sealed axle sleeve 118 and first step 1221 and the second step 1222, through the inside cushion chamber 1141 that forms and balance tube 130 intercommunication in butt wall 119, and communicate cushion chamber 1141 and balance chamber 114 through air vent 1191, make high-pressure gas in high-pressure chamber 113 can enter into cushion chamber 1141 at first through balance tube 130, then enter into balance chamber 114 through air vent 1191 and provide the second equilibrium for rotor 120, cushion chamber 1141 can play good cushioning effect, avoid causing the second equilibrium that rotor 120 received because of high-pressure gas's atmospheric pressure value changes greatly and break away, and then influence rotor 120's structural stability.

Referring again to fig. 1, in some embodiments of the present application, the balance pipe 130 is provided with a regulating valve 131.

Specifically, the adjusting valve 131 may be a manual adjusting valve or an automatic adjusting valve, and is not limited herein.

The regulating valve 131 is arranged on the balance pipe 130, so that the amount of high-pressure gas entering the balance cavity 114 can be controlled, the control and regulation of the second balance force on the rotor 120 are realized, and the axial stress balance stability of the rotor 120 in the operation process is ensured.

Referring to fig. 1, in some embodiments of the present disclosure, the housing 110 is provided with a thrust bearing 141, the rotor 120 is provided with a thrust disc 142, and the thrust disc 142 is connected to the thrust bearing 141 for limiting the axial displacement of the rotor 120.

When the axial thrust of the compressed high-pressure gas acting on the rotor 120 in the x-axis direction is equal to the sum of the first balance force and the second balance force, as shown in fig. 1, the thrust disk 142 does not contact and rub the thrust bearing 141 as shown in the drawing; when the axial thrust of the compressed high-pressure gas acting on the rotor 120 along the x-axis direction in the figure is greater than the sum of the first balance force and the second balance force, the left side of the thrust disk 142 abuts against and rubs against the thrust bearing 141 to limit the axial displacement of the rotor 120 along the x-axis direction; when the axial thrust of the compressed high-pressure gas acting on the rotor 120 in the x-axis direction in the drawing is smaller than the sum of the first balance force and the second balance force, the right side of the thrust disk 142 abuts against and rubs against the thrust bearing 141 to restrict the axial displacement of the rotor 120 in the direction opposite to the x-axis direction.

In a preferred embodiment, temperature measuring elements, such as temperature sensors, may be disposed on the bearing pads on both sides of the thrust bearing 141, and an operator may determine which side of the thrust bearing 141 is subjected to friction by observing and comparing the temperatures of the bearing pads on both sides of the thrust bearing 141, so as to determine the magnitude relationship between the axial thrust of the high-pressure gas to the rotor 120 and the sum of the first balance force and the second balance force, and control the opening and closing of the regulating valve 131 on the balance pipe 130 and the size of the opening area of the passage according to the magnitude relationship, so as to ensure that the thrust disc 142 may be located in the middle of the thrust bearing 141, and further ensure the axial balance of the rotor 120.

In other embodiments, a shaft displacement probe may also be provided on the rotor 120, and in particular, when the thrust bearing 141 is provided on the rotor 120 at a position close to the intake side as shown in fig. 1, the shaft displacement probe may be provided at an end of the rotor 120 close to the thrust bearing 141 side, i.e., an end on the left side of the rotor 120 in fig. 1. It is understood that when the thrust bearing 141 is provided at a position of the rotor 120 near the exhaust side (i.e., the thrust bearing 141 is provided at a position on the rotor 120 that is mirror-symmetrical to the position shown in fig. 1), the shaft displacement probe may be provided at an end of the rotor 120 near the thrust bearing 141 side, i.e., at an end on the right side of the rotor 120 in fig. 1. The axial displacement probe detects which side of the thrust bearing 141 the thrust disc 142 is closer to, and then confirms the magnitude relation between the axial thrust of the high-pressure gas to the rotor 120 and the sum of the first balance force and the second balance force, and adjusts the magnitude of the second balance force according to the magnitude relation.

Specifically, the inflow amount of the high-pressure gas may be reduced by increasing or decreasing the opening degree of the regulating valve 131 to increase or decrease the second balance force, and the high-pressure gas may not enter the balance chamber 114 by closing the regulating valve 131 to cancel the second balance force. By increasing, decreasing or eliminating the second balance force, the axial stress of the rotor 120 is adjusted, and the balance of the axial stress of the rotor 120 is ensured.

Referring to fig. 1, in some embodiments of the present application, a bearing 150 is disposed on the housing 110, and two ends of the rotor 120 are connected to the bearing 150.

By arranging the bearing 150 on the housing 110, the two ends of the rotor 120 are connected with the bearing 150 in a matching manner, so that the rotor 120 is supported by the housing 110 and the rotor 120 can normally run.

Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art will understand that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; such modifications and substitutions do not depart from the spirit and scope of the present invention, and they should be construed as being included in the following claims and description. In particular, the technical features mentioned in the embodiments can be combined in any way as long as there is no structural conflict. It is intended that the utility model not be limited to the particular embodiments disclosed, but that the utility model will include all embodiments falling within the scope of the appended claims.

Claims (10)

1. A compressor, comprising: a housing and a rotor;

the rotor is arranged on the shell in a penetrating mode, a low-pressure cavity, a compression cavity and a high-pressure cavity are sequentially formed between the rotor and the shell along the axial direction, and when the rotor rotates relative to the shell, low-pressure gas in the low-pressure cavity flows into the compression cavity and is compressed to form high-pressure gas and enters the high-pressure cavity;

the rotor is provided with a balance hub at the high-pressure cavity, so that high-pressure gas flowing out of the compression cavity provides a first balance force to the rotor from the low-pressure cavity to the high-pressure cavity through the balance hub;

the rotor is provided with a stress part, a balance cavity is formed between the stress part and the shell, the balance cavity is located on one side, away from the compression cavity, of the low-pressure cavity in the axial direction of the rotor, a balance pipe is connected between the high-pressure cavity and the balance cavity, so that part of high-pressure gas in the high-pressure cavity flows into the balance cavity through the balance pipe, and second balance force in the direction from the low-pressure cavity to the high-pressure cavity is provided for the rotor through the stress part.

2. The compressor of claim 1, wherein the balance hub includes a cylindrical section and a stage section having a side edge that is linear, the stage section being located between the cylindrical section and the compression chamber in the axial direction of the rotor, the stage section having a diameter that gradually increases from one end near the compression chamber to the other end.

3. The compressor of claim 1, wherein the balance hub includes a cylindrical section and a table section having a side edge that is curved, the table section being located between the cylindrical section and the compression chamber in the axial direction of the rotor, the table section having a diameter that gradually increases from one end near the compression chamber to the other end.

4. A compressor according to claim 2 or 3, wherein the cylindrical section is sealingly connected to the housing.

5. The compressor of claim 1, wherein the force receiving portion includes a first step and a second step, the first step and the second step are both in sealing connection with the shell, and the balance cavity is formed between the first step, the second step and the shell;

the high-pressure gas of the balance cavity provides the second balance force for the rotor by applying a force in a direction from the low-pressure cavity to the high-pressure cavity to a surface of the second step adjacent to the first step.

6. The compressor of claim 5, wherein the housing includes a seal bushing sealingly coupled to the first step and the second step, respectively, the seal bushing, the first step and the second step forming the balance cavity therebetween.

7. The compressor of claim 6, wherein the housing further comprises an abutment wall, the abutment wall being in abutment with the seal bushing, the abutment wall having a buffer chamber formed therein, the balance tube being in communication with the buffer chamber;

the butt joint wall with all be provided with the air vent on the sealed shaft sleeve, the air vent will the cushion chamber with balanced chamber intercommunication.

8. The compressor of claim 1, wherein the balance tube has a regulating valve disposed thereon.

9. The compressor of claim 1, wherein the housing is provided with a thrust bearing, and the rotor is provided with a thrust disc, the thrust disc being cooperatively connected with the thrust bearing for limiting axial displacement of the rotor.

10. The compressor of claim 1, wherein the housing is provided with a bearing, and both ends of the rotor are connected with the bearing in a matching manner.

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